Link suspension system

ABSTRACT

A bicycle includes a frame having a longitudinal axis, a first member, and a first pivot link assembly including a first link configured to rotate around a first pivot point. The first pivot point may have a first axis of rotation that is non-orthogonal to the longitudinal axis of the first frame, and the first frame may be coupled with the first member through the first pivot link assembly. Some examples also include a second pivot link assembly including a second link configured to rotate around a second pivot point having an axis of rotation that is non-orthogonal to the longitudinal axis of the frame.

CROSS REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of priority pursuant to 35 U.S.C.§119(e) of U.S. provisional application No. 61/375,278 filed 20 Aug.2010 entitled “Link Suspension System,” which is hereby incorporatedherein by reference in its entirety.

BACKGROUND

1. Technical Field

Examples disclosed herein relate generally to bicycles, and moreparticularly, to suspension systems for rear wheels of bicycles.

2. Background

Many bicycles, particularly mountain bicycles, include rear suspensionsystems. The rear suspension system allows the rear wheel to bedisplaced relative to the bicycle frame when impact forces are impartedon the rear wheel and, in turn, acts to absorb the impact forces. Assuch, suspension systems may improve rider comfort, as well as protectthe rider and all or part of the bicycle from the roughness of theterrain when traveling or jumping the bicycle by keeping one or bothwheels in contact with the ground and allowing the rider's mass to moveover the ground in a flatter trajectory.

Many rear suspension systems available on the market allow the rearwheel of the bicycle to travel in a particular path that is dictated bythe physical construction of the suspension system. Generally, the rearwheel path is fixed by the rear suspension design, with different rearwheel paths causing different reactions in the way that the bicyclehandles forces impacting on the rear wheel. The rear suspension systemsof different bicycles may have different shock-absorbing properties, soas to provide the dampening effect that is best suited to the terrainmost often traversed by the bicycle. A mountain bicycle intended fortraversing steep downhill grades may benefit from a shock assembly thatcauses the rear wheel to travel in a substantially vertical direction,while a trail bicycle intended for traversing small bumps and gradualdownhill grades may benefit from a shock that travels in a curved travelpath.

3. Summary

One aspect of the present disclosure relates to a rear suspension systemfor a bicycle. The rear suspension system acts to absorb forcesimpacting on the bicycle by allowing a rear wheel of the bicycle to bedisplaced relative to the rest of the bicycle. The structural andgeometrical configurations of some of the disclosed rear suspensionsystems provide a travel path in which the rear wheel moves along asubstantially linear travel path and in a substantially verticalorientation relative to the ground. Other disclosed examples includerear suspension systems that provide a travel path that is curved, withdifferent curves resulting from differences in the structural andgeometrical configurations of the systems.

Generally, examples described herein may take the form of a bicycleincluding a frame having a longitudinal axis, a first member, and afirst pivot link assembly including a first link configured to rotatearound a first pivot point. The first pivot point may have a first axisof rotation that is non-orthogonal to the longitudinal axis of the firstframe. The first frame may be coupled with the first member through thefirst pivot link assembly.

Another example of the bicycle may include a second pivot link assemblyincluding a second link configured to rotate around a second pivotpoint. The second pivot point may have a second axis of rotation that isnon-orthogonal to the longitudinal axis of the first frame. The firstframe may be additionally coupled with the first member through thesecond pivot link assembly. In another example, the second axis ofrotation may be oriented in a different direction than the first axis ofrotation. In a further example, the first axis of rotation and thelongitudinal axis may define a first angle therebetween that is between0 and 90 degrees. Additionally, the second axis of rotation and thelongitudinal axis may define a second angle therebetween that is between0 and 90 degrees. In addition, the first angle and the second angle maybe substantially equal.

In another example, the first link may be further configured to rotatearound a third pivot point having a third axis of rotation that issubstantially parallel to the first axis of rotation. In a furtherexample, the first pivot link assembly may further include a third linkconfigured to rotate around the third pivot point. In one example, thethird link may be further configured to rotate around a fourth pivotpoint having a fourth axis of rotation that is substantially parallel tothe first axis of rotation. The second link may be further configured torotate around a fifth pivot point having a fifth axis of rotation thatis substantially parallel to the second axis of rotation.

Another example may take the form of a bicycle comprising a frame, afront wheel rotatably connected with the frame, a rear suspensionsystem, and a rear wheel rotatably connected with the rear suspensionsystem. The rear wheel may be configured to rotate around a first axisof rotation. The rear suspension system may comprise a first member, afirst pivot link assembly operably coupling the first member with theframe and extending in a first direction that is non-orthogonal to thefirst axis of rotation, and a second pivot link assembly operablycoupling the first member with the frame and extending in a seconddirection different from the first direction that is non-orthogonal tothe first axis of rotation. In one example, the first pivot linkassembly may extend diagonally relative to the second pivot linkassembly.

Another example may take the form of a bicycle comprising a frame havinga longitudinal axis and including a head tube, a top tube connected withthe head tube, a down tube connected with the head tube, and a bottombracket connected with the down tube. The bicycle may further include afront wheel operably coupled with the head tube, and a rear suspensionsystem including a swingarm and a first pivot link assembly pivotallyconnected to the swingarm and to the frame. The first pivot linkassembly may include a first link configured to rotate around a firstpivot point having a first axis of rotation that is non-orthogonal tothe longitudinal axis of the frame.

Yet another example may take the form of a suspension system for abicycle. The system may include a first pivot link assembly configuredto couple a first member to a frame having a longitudinal axis and asecond pivot link assembly configured to couple the first member to theframe. The first pivot link assembly may include a first link configuredto rotate around a first pivot point. The first link may define a firstangle relative to the frame. The second pivot link assembly may includea second link configured to rotate around a second pivot point. Thesecond link may define a second angle relative to the frame. The firstand second angles may be substantially equal.

A further example may take the form of a suspension system including afront frame having a longitudinal axis and a link suspension systemoperably coupled to the front frame. The link suspension system mayinclude a first pivot link assembly including a first forward link and afirst rear link configured to pivot relative to the first forward link,where an axis of rotation of the first rear link relative to the firstforward link is non-orthogonal to the longitudinal axis of the frontframe. The link suspension system may further include a second pivotlink assembly including a second forward link and a second rear linkconfigured to pivot relative to the second forward link, where an axisof rotation of the second rear link relative to the second forward linkis non-orthogonal to the longitudinal axis of the front frame. One endof each of the pivot link assemblies of the link suspension systemdefines a fixed pivot point relative to the front frame and the otherend of each of the pivot link assemblies of the link suspension systemdefines a pivot point relative to the front frame.

In other examples, the suspension system may further include a rearframe operably coupled to the front frame. In another example, a firstforward end of the first pivot link assembly is pivotally coupled to thefront frame and a first rear end of the first pivot link assembly ispivotally coupled to the rear frame, and a second forward end of thesecond pivot link assembly is pivotally coupled to the front frame and asecond rear end of the second pivot link assembly is operably coupled tothe rear frame. In another example, the first and second rear ends ofthe first and second pivot link assemblies are configured to travelalong a substantially linear path.

In a further example, the first and second rear ends of the first andsecond pivot link assemblies are pivotally coupled to a mounting bracketthat is coupled to the rear frame. Another example may include a shocklink having a first end pivotally coupled to the front frame and asecond end pivotally coupled to the rear frame. Further examples mayinclude a shock having a first end pivotally coupled to the front frameand a second end pivotally coupled to the rear frame.

In another example, the shock link may be configured to rotate in aclockwise direction. Additionally, the shock link may be configured torotate in a counterclockwise direction. In another example, the secondend of the shock is further pivotally coupled to the second end of theshock link. Another example may include a shock having a first endpivotally coupled to the front frame and a second end pivotally coupledto the mounting bracket. In some examples, the shock is substantiallyparallel to the substantially linear path defined by the first andsecond pivot link assemblies. The shock link may be configured to rotatein a clockwise direction in some examples, and in a counter-clockwisedirection in other examples.

Yet another example may take the form of a bicycle including a framehaving a longitudinal axis, a first pivot link assembly including afirst link configured to rotate around a first pivot point, where thefirst pivot point has a first axis of rotation that is non-orthogonal tothe longitudinal axis of the first frame. The pivot link assembly mayfurther include a second pivot link assembly including a second linkconfigured to rotate around a second pivot point, where the second pivotpoint has a second axis of rotation that is non-orthogonal to thelongitudinal axis of the first frame, and a shock assembly having afirst end coupled to the first pivot link and a second end coupled tothe second pivot link.

Other examples of the bicycle may include a first member, where thefirst frame is coupled with the first member through the first pivotlink assembly. In a further example, the shock assembly is configured totravel in three dimensions. In another example, the first end of theshock is configured to travel along a first plane that is parallel to asecond plane defined by the first pivot link assembly. In some examples,the first pivot link assembly further includes a third link configuredto rotate around the first link, and the second pivot link assemblyfurther includes a fourth link configured to rotate around the thirdlink.

In further examples, the third link is positioned behind the first linkand the second link is positioned behind the fourth link. Additionally,in some examples, the first and second links are pivotally coupled tothe front frame and the third and fourth links are pivotally coupled toa rear frame.

Another example may take the form of a bicycle including a frame havinga longitudinal axis and a shock operably associated with the frame, theshock operably associated with the frame and having a first endconfigured to travel along a first plane and a second end configured totravel along a second plane that intersects the first plane.

In another example, the first end of the shock is coupled to a firstlink oriented at a first angle with respect to the frame and the secondend of the shock is coupled to a second link oriented at a second anglewith respect to the frame. Another example may further include a thirdlink pivotally coupled to the first link, where an axis of rotation ofthe third link around the first link is non-orthogonal to the frame. Afurther example may include a fourth link pivotally coupled to thesecond link, where an axis of rotation of the fourth link around thesecond link is non-orthogonal to the frame. A further example mayinclude a rear frame pivotally coupled to the third link and to thefourth link, where the rear frame is configured to travel, and thetranslation of the rear frame is substantially confined to a singleplane.

Another example may take the form of a bicycle including a front frame,a rear frame operably associated with the front frame, and a suspensionsystem operably coupled to the front frame and to the rear frame andincluding a shock assembly. The suspension system causes at least aportion of the rear frame to travel in a first direction and in a seconddirection opposite the first direction during a single compression of ashock assembly.

In a further example, the portion of the rear frame is configured totravel along a substantially linear path.

Another example may take the form of a bicycle including a front framehaving a longitudinal axis, a rear frame operably associated with thefront frame and to a wheel, and a suspension system operably coupled tothe front frame and to the rear frame. The suspension system causes atleast a portion of the rear frame to travel in a first direction and ina second direction opposite the first direction as the wheel travels inan upward direction relative to the front frame.

In other examples, the curvature of the wheel increases as the wheeltravels in the upward direction. In another example, the suspensionsystem includes a first pivot link assembly including a first linkconfigured to rotate around a first pivot point. The first pivot pointhas a first axis of rotation that is non-orthogonal to the longitudinalaxis of the frame. The suspension system further includes second pivotlink assembly including a second link configured to rotate around asecond pivot point, the second pivot point having a second axis ofrotation that is non-orthogonal to the longitudinal axis of the frame.

Another example may take the form of a mounting assembly including afirst member coupled to an supported object, a second member coupled toa supporting object, a first pivot link assembly coupled between thefirst member and the second member, and a second pivot link assemblycoupled between the first member and the second member. The first pivotlink assembly may include a first link pivotally coupled to a secondlink, and the second pivot link assembly comprising a third linkpivotally coupled to a fourth link. The first and second pivot linkassemblies allow for moving the supported object away from thesupporting object along a substantially linear path.

The features, utilities, and advantages of the various disclosedexamples will be apparent from the following more particular descriptionof the examples as illustrated in the accompanying drawings and definedin the appended claims.

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a right side view of a bicycle incorporating a rear suspensionsystem according to one example.

FIG. 2 is a right-front isometric view of a front frame and rearsuspension system of the bicycle depicted in FIG. 1.

FIG. 3 is a right-bottom isometric view of the front frame and rearsuspension system of the bicycle depicted in FIG. 1.

FIG. 4 is a bottom view of the front frame and rear suspension system ofthe bicycle depicted in FIG. 1 with the bottom bracket partiallyremoved.

FIG. 5 is a top view of the front frame and rear suspension system ofthe bicycle depicted in FIG. 1 with the seat tube and top bracketpartially removed.

FIG. 6 is a right side view of a front frame and rear suspension systemof the bicycle depicted in FIG. 1.

FIG. 7A is a right side view of the front frame of the bicycle depictedin FIG. 1, and FIG. 7B is a partial cross-sectional view of the seattube, as taken along line 7B-7B of FIG. 7 a.

FIG. 8A is a right side view of the rear suspension system of thebicycle depicted and FIG. 8B is a partial cross-sectional view of therear link of the first pivot link assembly, as taken along line 8B-8B ofFIG. 8A.

FIG. 9 is a rear view of the front frame and rear suspension system ofthe bicycle depicted in FIG. 1 in an uncompressed stage shown in solidlines, and in a fully compressed stage shown in dashed lines.

FIG. 10 is right side view of the front frame and rear suspension systemof the bicycle depicted in FIG. 1, with the shock in a partiallycompressed position.

FIG. 11 is a rear view of the front frame and rear suspension system ofthe bicycle depicted in FIG. 1, with the shock in a partially compressedposition.

FIG. 12 is a right side view of the front frame and rear suspensionsystem of the bicycle depicted in FIG. 1, with the shock in a fullycompressed position.

FIG. 13 is a rear view of the front frame and rear suspension system ofthe bicycle depicted in FIG. 1, with the shock in a fully compressedposition.

FIG. 14 is a right side view of the rear suspension system in anuncompressed stage shown in solid lines, and in a partially compressedstage and a fully compressed stage shown in dashed lines.

FIG. 15 is a right-front isometric view of a front frame and a rearsuspension system according to a second example of the presentinvention.

FIG. 16A is a right-front isometric view of a front frame and rearsuspension system according to a third example of the present invention.

FIG. 16B is a right side view of the rear suspension system depicted inFIG. 16A in an uncompressed stage shown in solid lines, and in apartially compressed stage and a fully compressed stage shown in dashedlines.

FIG. 17A is a right side view of a front frame and rear suspensionsystem according to a fourth example of the present invention.

FIG. 17B is a right-front isometric view of the front frame and rearsuspension system depicted in FIG. 17A.

FIG. 17C is a right side view of the front frame and rear suspensionsystem depicted in FIG. 17A in a fully compressed stage.

FIG. 17D is a right side view of the front frame and rear suspensionsystem depicted in FIG. 17A in an uncompressed stage shown in solidlines, and in a fully compressed stage shown in dashed lines.

FIG. 17E is a right side view of the front frame depicted in FIG. 17A inan uncompressed stage.

FIG. 17F is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 17A in an uncompressedstage, as well as an outline of the rear frame.

FIG. 17G is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 17A in a fully compressedstage, as well as an outline of the rear frame.

FIG. 17H is a top down view of the front frame and rear suspensionsystem depicted in FIG. 17A in a fully compressed stage.

FIG. 17I is a cross-sectional view of the front frame and rearsuspension system depicted in FIG. 17A, as taken along line 17I-17I ofFIG. 17H.

FIG. 17J is a cross-sectional view of the front frame and rearsuspension system depicted in FIG. 17A, as taken along line 17J-17J ofFIG. 17H.

FIG. 18A is a right side view of a front frame and rear suspensionsystem according to a fifth example of the present invention.

FIG. 18B is a right-front isometric view of the front frame and rearsuspension system depicted in FIG. 18A.

FIG. 18C is a right side view of the front frame and rear suspensionsystem depicted in FIG. 18A in a fully compressed stage.

FIG. 18D is a right side view of the front frame and rear suspensionsystem depicted in FIG. 18A in an uncompressed stage shown in solidlines, and in a fully compressed stage shown in dashed lines.

FIG. 18E is a right side view of the front frame depicted in FIG. 18A ina fully compressed stage.

FIG. 18F is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 18A in an uncompressedstage, as well as an outline of the rear frame.

FIG. 18G is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 18A in a fully compressedstage, as well as an outline of the rear frame.

FIG. 19A is a right side view of a front frame and rear suspensionsystem according to a sixth example of the present invention.

FIG. 19B is a right-front isometric view of the front frame and rearsuspension system depicted in FIG. 19A.

FIG. 19C is a right side view of the front frame and rear suspensionsystem depicted in FIG. 19A in a fully compressed stage.

FIG. 19D is a right side view of the front frame and rear suspensionsystem depicted in FIG. 19A in an uncompressed stage shown in solidlines, and in a fully compressed stage shown in dashed lines.

FIG. 19E is a right side view of the front frame depicted in FIG. 19A ina fully compressed stage.

FIG. 19F is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 19A in an uncompressedstage, as well as an outline of the rear frame.

FIG. 19G is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 19A in a fully compressedstage, as well as an outline of the rear frame.

FIG. 20A is a right side view of a front frame and rear suspensionsystem according to a seventh example of the present invention.

FIG. 20B is a right-front isometric view of the front frame and rearsuspension system depicted in FIG. 20A.

FIG. 20C is a right side view of the front frame and rear suspensionsystem depicted in FIG. 20A in a fully compressed stage.

FIG. 20D is a right side view of the front frame and rear suspensionsystem depicted in FIG. 20A in an uncompressed stage shown in solidlines, and in a fully compressed stage shown in dashed lines.

FIG. 20E is a right side view of the front frame depicted in FIG. 20A ina fully compressed stage.

FIG. 20F is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 20A in an uncompressedstage, as well as an outline of the rear frame.

FIG. 20G is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 20A in a fully compressedstage as well as an outline of the rear frame.

FIG. 21A is a right-front isometric view of a front frame and rearsuspension system according to an eighth example of the presentinvention.

FIG. 21B is a top view of the front frame and rear suspension system ofthe front frame and rear suspension system depicted in FIG. 21A with theseat tube and top bracket partially removed.

FIG. 22A is a right-front isometric view of a front frame and rearsuspension system according to a ninth example of the present invention.

FIG. 22B is a top view of the front frame and rear suspension system ofthe front frame and rear suspension system depicted in FIG. 22A with theseat tube and top bracket partially removed.

FIG. 23A is a right-rear isometric view of a front frame and rearsuspension system according to a tenth example of the present invention.

FIG. 23B is a right side view of the front frame and rear suspensionsystem depicted in FIG. 23A.

FIG. 23C is a right side view of the front frame and rear suspensionsystem depicted in FIG. 23A in a partially compressed stage.

FIG. 23D is a right side view of the front frame and rear suspensionsystem depicted in FIG. 23A in an uncompressed stage shown in solidlines, and in a fully compressed stage shown in dashed lines.

FIG. 23E is a front view of the front frame and rear suspension systemdepicted in FIG. 23A in an uncompressed stage.

FIG. 23F is a front view of the front frame and rear suspension systemdepicted in FIG. 23A in a fully compressed stage.

FIG. 23G is a front view of the front frame and rear suspension systemdepicted in FIG. 23A in an uncompressed stage shown in solid lines, andin a fully compressed stage shown in dashed lines.

FIG. 23H is a top down view of the front frame and rear suspensionsystem depicted in FIG. 23A in an uncompressed stage shown in solidlines, and in a fully compressed stage shown in dashed lines.

FIG. 23I is a top down view of the front frame and rear suspensionsystem depicted in FIG. 23A in a fully compressed stage.

FIG. 23J is a front view of the front frame and rear suspension systemdepicted in FIG. 23A in an uncompressed stage.

FIG. 23K is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 23A in an uncompressedstage, as well as an outline of the rear frame.

FIG. 23L is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 23A in a partiallycompressed stage as well as an outline of the rear frame.

FIG. 23M is a top view of the front frame and rear suspension systemdepicted in FIG. 23A in an uncompressed stage shown in solid lines, andin a fully compressed stage shown in dashed lines.

FIG. 23N is a left side view of the front frame and rear suspensionsystem depicted in FIG. 23A in an uncompressed stage shown in solidlines, and in a partially compressed stage shown in dashed lines.

FIG. 23O is a rear view of the front frame and rear suspension systemdepicted in FIG. 23A in an uncompressed stage shown in solid lines, andin a partially compressed stage shown in dashed lines.

FIG. 24A is a right side view of a front frame and rear suspensionsystem according to an eleventh example of the present invention.

FIG. 24B is a right side view of the front frame and rear suspensionsystem depicted in FIG. 24A in a partially compressed stage.

FIG. 24C is a right side view of the front frame and rear suspensionsystem depicted in FIG. 24A in a fully compressed stage.

FIG. 24D is a right side view of the front frame and rear suspensionsystem depicted in FIG. 24A in an uncompressed stage shown in solidlines, in a partially compressed stage shown in dashed lines, and in afully compressed stage shown in dashed lines.

FIG. 24E illustrates a right side view of a portion of the mountingbracket in an uncompressed stage shown in solid lines, in a partiallycompressed stage shown in dashed lines, and in a fully compressed stageshown in dashed lines.

FIG. 24F is a right side view of the front frame depicted in FIG. 24A ina fully compressed stage.

FIG. 24G is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 24A in an uncompressedstage, as well as an outline of the rear frame.

FIG. 24H is a right side view of the shock and pivot link assemblies ofthe rear suspension system depicted in FIG. 24A in a fully compressedstage, as well as an outline of the rear frame.

FIG. 25A is a front view of a television mounted on a wall using anotherexample of a linkage system.

FIG. 25B is a top down view of the television, wall, and pivot linkassemblies depicted in FIG. 25A, where the linkage system is in anextended position.

FIG. 25C is a top down view of the television, wall, and pivot linkassemblies depicted in FIG. 25A, where the linkage system is in aretracted position.

FIG. 25D is a rear view of the television, wall, and pivot link assemblydepicted in FIG. 25A.

DETAILED DESCRIPTION

Generally, examples described herein take the form of a rear suspensionsystem for a bicycle. The rear suspension system acts to absorb forcesimpacting on the bicycle by allowing a rear wheel of the bicycle to bedisplaced relative to the rest of the bicycle. Such forces may be causedfrom riding over rough terrain (such as rocks, holes in the ground, andthe like). Upon displacement of the rear wheel, the rear suspensionsystem can allow the rear wheel to move from a general first position toa second position. The rear suspension system may then act to return therear wheel to the general first position. The structural and geometricalconfigurations of the rear suspension system provide a travel path inwhich the rear wheel moves when acted upon by various forces. Asdiscussed below, examples of the rear suspension system can include afirst pivot link assembly and a second pivot link assembly configured tocouple the front frame of the bicycle to the swingarm connected to therear wheel. The link assemblies may each include at least one link thatis configured to rotate around an axis of rotation that isnon-orthogonal to the longitudinal axis of the frame.

As is known in the art, the leverage ratio of a rear suspension systemalso can also affect the “feel” of the rear suspension system as sensedby the rider when the rear wheel is displaced. The leverage ratio can bedefined as the total rear wheel travel divided by the total shock strokelength, and changes instantaneously throughout the travel path of therear wheel. The instantaneous leverage ratios at different points alongthe travel path can be plotted to derive a leverage ratio curve.Generally, a suspension system having higher instantaneous leverageratios results in an increased mechanical advantage at the rear wheel,allowing for a “softer” suspension, while a system having lowerinstantaneous leverage ratios results in a decreased mechanicaladvantage at the rear wheel, allowing for a “firmer” suspension.Different types of leverage ratio curves may be better suited for usewith different types of shock assemblies (e.g., an air or liquid shockvs. a spring shock), and with different types of bicycles (e.g., dirtbikes, mountain bikes, road bikes, downhill hikes, cross-country bikes,and so on), to provide a more comfortable riding experience.

Examples of the rear suspension system may be capable of traveling alonga substantially linear and vertical path. The rear suspension system mayhave a 1:1 leverage ratio and maximize the efficiency of the rearsuspension system. Although the rear suspension system is describedbelow with reference to a typical bicycle depicted in the figures, itshould be understood the rear suspension system can be used withbicycles having different frame styles than that which is depicted anddescribed herein. Further, although the systems and methods aredescribed below mainly with reference to bicycles, the present inventioncan be applied to other vehicles, such as scooters and motorcycles.

FIG. 1 shows a bicycle 100 including a rear suspension system 102according to a first example. The bicycle 100 is rollingly supported bya front wheel 104 and a rear wheel 106. A rider can steer the bicycle100 by turning the front wheel 104 toward a desired direction of travelwith a steering system 108. The bicycle 100 also includes a seat 110connected with a front frame 112 which can be used to support the rider.As discussed in more detail below, the rear suspension system includes aswingarm 114 coupled with the front frame 112 through a link suspensionsystem 115 including a first link assembly 116, a second link assembly118, and a shock assembly 120, which may be operably connected betweenthe front frame 112 and the swingarm 114. The swingarm may be fabricatedfrom various members connected together, or as a single piece or member.The swing arm may be one-sided or two-sided.

As shown in FIGS. 1-3, the front frame 112 can include a head tube 122,a top tube 124, a down tube 126, a bottom bracket 128, and a seat tube130. The top tube 124 extends rearwardly from the head tube 122 toconnect with an upper portion of the seat tube 130, and the down tube126 extends rearwardly and downwardly from the head tube 122 to connectwith the bottom bracket 128. The front frame 112 described hereinutilizes a continuous seat tube design where the seat tube 130 extendsfrom the top tube 124 all the way to the down tube 126. It is to beappreciated that in other frame configurations, the seat tube mayinclude an interrupted design in which the seat tube does not fullyextend from the top tube to connect with the down tube. Referring toFIG. 1, the seat or saddle 110, which is used to support the rider, isconnected with a seat post 132 that may be inserted into the seat tube130. In some configurations, the seat post can be adjustably orreleasably received within the seat tube 130, for example, so the heightof the seat relative to the front frame 112 can be adjusted.

As illustrated in FIG. 1, the steering system 108 includes a handle bar134 connected with an upper portion of a front fork member 136. Both thehandle bar 134 and the front fork member 136 are rotatably connectedwith the head tube 122. The front wheel 104 is rotatably connected witha lower portion of the front fork member 136, as is known in the art.Turning the handle bar 134 in a particular direction causes the frontwheel 104 to turn in the same direction. As such, a user can steer thebicycle 100 by turning the handle bar 134 in a desired direction oftravel.

As described in more detail below, the rear wheel 106 may be rotatablyconnected with the swingarm 114 through a rear axle 138. It is to beappreciated that the rear axle 138 may be connected to the swingarm 114in many ways, such as by use of drop-out structures or the like, as areknown.

As shown in FIGS. 1-3, the bottom bracket 128 is connected with a lowerend portion of the down tube 126. The bottom bracket 128 rotatablysupports a crank shaft 140 having crank arms 142 extending radiallytherefrom in opposite directions. Foot pedals 144 are rotatablyconnected with the crank arms. A drive sprocket 146, which is connectedwith the crank shaft 140, is typically connected through a chain 148with a rear sprocket assembly 150 coupled with the rear wheel 106. Whenthe rider applies forces to the pedals 144, the forces may be translatedthrough the drive sprocket 146 and chain 148 to the rear sprocketassembly 150, causing the rear wheel 106 to rotate. Rotation of the rearwheel 106 may translate into forward motion of the bicycle 100.

As shown in FIGS. 2-5 and 8, the swingarm 114 includes right and leftarms 152, 154, typically referred to as chain stays. Generally, theright and left arms 152, 154 are connected together by a centralattachment member 153 that may also be attached to the first linkassembly 116 and the second link assembly 118. Because the right andleft arms 152, 154 are substantially mirror images of each other,descriptions with reference to the right arm 152, are applicable to theleft arm 154 unless otherwise noted. As shown in FIGS. 2 and 3, the rearend portions of the right and left arms 152, 154 are each connected to arespective rear joint member 168, 170. Right and left rear joint members168, 170 include rear axle apertures 172 adapted to receive androtatably support the rear axle 138 of the rear wheel 106. As is known,some examples may further include dropouts to allow for detaching theaxle 138 of the wheel 106 from the swingarm 114. It is to be appreciatedthat the swingarm 114 can be constructed from various types of material,such as aluminum, carbon, or titanium. The members used to construct theswingarm may also define a hollow tubular structure, or may have a solidconstruction, or other suitable construction. The swing arm may beconstructed to facilitate the use of disc brakes, and a derailleurstructure.

The forward end portions of the right and left arms 152, 154 areconnected with the central attachment member 153, which may beintegrally formed with the arms or a separate part attachable to thearms. As will be further discussed below, the central attachment member153 may define right and left link attachment portions 167, 169 to whichfirst and second pivot link assemblies 116, 118 are pivotally attached.In particular, the first and second link assemblies 116, 118 may berotatably mounted to the link attachment portions 167, 169, therebyconnecting the swingarm 114 with the down tube 126 of the front frame112. The central attachment member 153 may also include an axle 161adapted to connect to the bottom end of the shock assembly 120 to couplethe shock assembly 120 to the central attachment member 153, describedin more detail below. The link suspension system 115 may also generallyattached to the central member 153.

The top end of the shock 120 may be connected to the seat tube 130 viaan axle 300 mounted on the top end of the piston shaft 314 andcorresponding receiving apertures 302 defined by the seat tube 130. Asdiscussed above, the bottom end of the shock 120 may be connected to thecentral attachment member 153. In one example, the shock 120 may besubstantially parallel to the y-axis when mounted to the seat tube 130and to the central attachment member 153, so as to be positioned in asubstantially vertical orientation. However, in other examples, theshock 120 may be positioned at an angle relative to the y-axis. Forexample, the shock 120 may be positioned so as to define an anglebetween 0 and 90 degrees with respect to the y-axis. As will be furtherdiscussed below, in one example, the position of the shock 120 relativeto the front frame 112 may partially define the path traversed by theswing arm 114 and the rear wheel 106 when the shock 120 is compressed.However, in other examples, the path traversed by the swing arm 114 maybe substantially wholly defined by the first and second link assemblies116, 118, which may serve to constrain the motion of the swing arm 114to a substantially linear path.

The shock assembly 120 may include a piston shaft 314 and a cylinderbody 306. Generally, compression of the shock assembly 120 causes thecylinder body 306 to be pushed in an upward direction over the shaft314, for example, as the rear wheel 106 is displaced relative to thefront frame 112. Fluid contained within the cylinder body 306 acts todampen the movement of the piston shaft 314 within the cylinder body. Assuch, the shock 120 dampens the tensile and/or compressive forcesexerted on the piston shaft 314. The shock assembly 120 may be placed invarious stages of compression relative to the amount of upward forceapplied to the bottom end of the shock assembly 120. For example, alarger upward force applied to the bottom end of the shock assembly 120may cause the cylinder body 306 to traverse a longer length of thepiston shaft 314 than a smaller upward force. As shown in FIGS. 7A-7B,the seat tube 130 may define a recessed portion 310 that is configuredto receive the cylinder body 306 so that the upper portion of thecylinder body 306 is partially retracted into the recessed portion 310when the shock assembly 120 is in a fully compressed stage. It is to beappreciated that shock assemblies are known in the art and that varioustypes of shock assemblies and orientation can be utilized with thepresent disclosure. Some examples of shock assemblies include oilshocks, air shocks, spring return shocks, gas charged shocks, and so on.

The first and second pivot link assemblies 116, 118 will now bedescribed in more detail. As shown in FIGS. 1-6, the first pivot linkassembly 116 may include a rear link 117 that is pivotally connected toa forward link 119. The front end of the forward link 119 may bepivotally connected to the front frame 112 and the rear end of theforward link 119 may be pivotally connected with the front end of therear link 117. The rear end of the rear link 117 may be pivotallyconnected to the right link attachment portion 167 of the swingarm 114.Accordingly, the first pivot link assembly 116 may define three pivotpoints 182, 185, and 187. The second pivot link assembly 118 may besimilar in configuration to the first pivot link assembly 116. Forexample, the second pivot link assembly 118 may also include a rear link127 that is pivotally connected to a forward link 129. The front end ofthe forward link 129 may be pivotally connected with the front frame 112and the rear end of the forward link 119 may be pivotally connected tothe front end of the rear link 117. The rear end of the rear link 117may be pivotally connected to the left link attachment portion 169 ofthe swingarm 114. The second pivot link assembly 118 may define threepivot points 194, 198, and 206.

As shown in FIGS. 5, 6 and 7 the down tube 126 may include atriangular-shaped mounting portion 200 defining right and left mountingarms 210, 212 to which the first pivot link assembly 116 and the secondpivot link assembly 118 are pivotally attached. The right and leftmounting arms 210, 212 may each include an angled mounting surface 214.As best shown in FIGS. 5 and 7, each mounting surface 214 may define anangle A, B that is between 0 and 90 degrees with respect to thelongitudinal axis of the frame, i.e., the x-axis. In other examples,mounting portion 200 may have a different configuration, for example,the mounting portion 200 may have a different polygonal configuration,or may have a rounded shape. Additionally, in other examples, eachmounting surface 214 may define an angle between 90 to 180 degrees withrespect to the longitudinal axis of the frame and to the x-axis, orbetween 180 to 270 or 270 to 360 degrees with respect to thelongitudinal axis of the frame and to the x-axis.

As best shown in FIGS. 4-8, the first and second pivot link assemblies116, 118 may be positioned in a crossed, or x-shaped configuration. Thex-shaped configuration of the link assemblies 116, 118 may serve toreduce the amount of space required for operation of the first andsecond pivot link assemblies 116, 118 and maintain the streamlinedprofile of the bicycle. For example, as shown in FIG. 5, the first pivotlink assembly 116 may extend transversely from the right link attachmentportion 167 of the central attachment member 153 to the left mountingarm 210 of the mounting portion 200 to define an angle A, that isbetween 0 and 90 degrees with respect to the longitudinal axis of theframe and to the x-axis. In other examples, the first pivot linkassembly 116 may extend between 90 to 180 degrees with respect to thelongitudinal axis of the frame and to the x-axis, or between 180 to 270or 270 to 360 degrees with respect to the longitudinal axis of the frameand to the x-axis, so long as the pivot link assemblies 116, 118 are notparallel in orientation. Stated another way, the first pivot linkassembly 116 may extend in a first direction that is non-orthogonal tothe z-axis (see FIG. 5) and the axis of rotation of the rear wheel.Furthermore, as shown in FIG. 4, the axes of rotation AR1, AR2, AR3 ofthe forward and rear links 117, 119 around the pivot points 182, 185,187 may be orthogonal to the orientation of the links, and may furtherbe non-orthogonal to the longitudinal axis of the frame 112. Moreparticularly, the axes of rotation AR1, AR2, AR3 of the links 117, 119around the pivot points 182, 185, 187 may form an angle that is between0 and 90 degrees with respect to the longitudinal axis of the frame 112(the x-direction). In other examples, the axes of rotation, may form anangle between 90 to 180 degrees with respect to the longitudinal axis ofthe frame and to the x-axis, or between 180 to 270 or 270 to 360 degreeswith respect to the longitudinal axis of the frame and to the x-axis.

Similarly, the second pivot link assembly 118 may extend over or underthe first pivot link assembly 116 from the left link attachment portion169 of the central attachment member 153 to the right mounting arm 212of the mounting portion 200 to define an angle B with respect to thelongitudinal axis of the frame. Accordingly, the direction of extensionof the second pivot link assembly 118 may be non-orthogonal to thez-axis and the axis of rotation of the rear wheel. Further, as shown inFIG. 4, the axes of rotation AR4, AR5, AR6 of the forward and rear links127, 129 around the pivot points 194, 198, 206 may be orthogonal to theorientation of the links 127, 129 and non-orthogonal to the longitudinalaxis of the frame 112 (the x-direction). As shown in FIG. 5, the angle Bdefined between the second pivot link assembly 118 and the x-axis may beequal to the angle A defined between the first pivot link assembly 116and the x-axis, thereby equalizing the distribution of forces along thefirst and second pivot link assemblies 118.

It is to be appreciated that the relative positions of the first andsecond pivot link assemblies 116, 118 with respect to one another is notcritical. For example, in one example, the second pivot link assembly118 may extend over and across the second pivot link assembly 116,generally forming an X-shape when viewed from above, while in otherexamples, the positions of the first and second pivot link assemblies116, 118 may be reversed so that the first pivot link assembly 116extends over the second pivot link assembly 118. The positioning of thefirst and second pivot link assemblies 116, 118 along the swing arm 114and the front frame 112 is also not critical. For example, in otherexamples, the first and second pivot link assemblies 116, 118 may bemounted anywhere along the length of the swingarm 114 and/or the frontframe 112. Also, the pivot link assemblies may be mounted so that theydo not cross over one another, for example, too form a V-shape whenviewed from above.

The transverse orientation of the link assemblies 116, 118 serves torestrict horizontal movement of the swingarm 114 along the z-axis,thereby controlling, inhibiting, or preventing side-to-side wobbling ofthe swingarm 114 and the connected rear wheel 106. Each of the linkassemblies 116, 118 serve as yokes to counterbalance the load caused byside-to-side deflection of the swingarm 114. More particularly, thefirst link assembly 116 may provide an opposing force to counterbalancemovement of the swingarm 114 to the left, while the second link assembly118 may provide an opposing force to counterbalance movement of theswingarm 114 to the right. Accordingly, as shown in FIG. 9, the swingarm114 is prevented from moving back and forth along the z-axis, andinstead travels along a travel path located along the X-Y-plane.

The transverse orientation of the link assemblies 116, 118 furtherconfines any motion of the swingarm 114 and the connected rear wheel 106to a substantially linear path having limited, if any, curvature.Referring to FIG. 6, the path traversed by the swingarm 114 may bedetermined by the angle defined between the shock 120 and the y-axis.Therefore, if the shock 120 is oriented so that it is parallel to they-axis, then the travel path of the swingarm 114 will be confined to alinear path that is substantially parallel to the y-axis. In thisconfiguration, the rear wheel 106 can travel in a substantially verticalorientation, allowing for a 1:1 leverage ratio and improving theefficiency of the shock 120 in absorbing forces exerted on the rearwheel 105. Furthermore, the Instant Center of Curvature (“ICC”) andInstant Center (“IC”) of the rear wheel 105 may approach infinitybecause the wheel path is completely linear. The IC is the point for theswingarm 114 as it is undergoing planar movement, i.e., during wheeltravel, which has zero velocity at a particular instant of time. At thisinstant the velocity vectors of the trajectories of other points in theswingarm generate a circular field around the IC, which is identical towhat is generated by a pure rotation. The ICC, as used herein, refers tothe ICC with respect to the center point of the rear wheel axle. The ICCcan be derived from the radius of curvature at given point along wheelpath, or the radius of a circle that mathematically best fits the curveof the wheel path at that point. The center point of this circle is theICC.

In other examples, the first and second pivot link assemblies 116, 118may define different angles with respect to the longitudinal axis of theframe, such that angle A and angle B, as shown in FIG. 5, may not besubstantially equal. In such examples, the forces impacting upon therear wheel may be distributed unevenly between the two pivot linkassemblies 116, 118. Nonetheless, the transverse orientation of the linkassemblies 116, 118 may serve to restrict horizontal movement of theswingarm 114 along the z-axis, with each of the link assemblies 116, 118providing counteracting forces to counterbalance the load caused byside-to-side deflection of the swingarm 114. Accordingly, the swingarm114 may be prevented from moving back and forth along the z-axis evenwhen the angles defined between the link assemblies 116, 118 and thelongitudinal axis of the frame are different. In one particular example,one of the pivot link assemblies may extend such that it issubstantially parallel to the longitudinal axis of the frame, and theother of the pivot link assemblies may extend such that it issubstantially orthogonal to the longitudinal axis of the frame.

Referring to FIG. 6, in another example, the shock 120 may be tiltedrearward to form an angle C with respect to the y-axis and the mountingpoints for the pivot link assemblies 116, 118 readjusted such that thelinear path defined by the pivot link assemblies 116, 118 is parallel tothe shock. In this example, the motion of the swingarm 114 may besubstantially confined to a linear path that forms an angle C withrespect to the y-axis, and the leverage ratio may be substantially closeto 1:1. Similarly, the shock 120 may be tilted forward to form an angleD with respect to the y-axis and the mounting points for the pivot linkassemblies 116, 118 readjusted such that the linear path defined by thepivot link assemblies 116, 118 is parallel to the shock. In thisexample, the motion of the swingarm 114 may be substantially confined toa linear path that forms an angle D with respect to the y-axis.Accordingly, the shock 120 may be tilted forward or backward so as todefine any angle between 0 and 90 degrees with respect to the y-axis andthe mounting points for the pivot link assemblies 116, 118 readjustedsuch that the linear path defined by the pivot link assemblies 116, 118is parallel to the shock, such that the wheel path also forms the sameangle with respect to the y-axis, and the leverage ratio is 1:1.

In other examples, the shock 120 may be oriented at an angle withrespect to the travel path of the rear wheel 105, i.e., so that theshock 120 and the travel path of the wheel 105 are no longer parallel,and the leverage ratio varies from 1:1. In such cases, the wheel traveldistance may be longer or shorter than the shock stroke length. As anexample, this may be accomplished by rotating the shock at an anglealong the Y-Z plane (i.e., such that the shock is not parallel to they-axis when viewed from the front of the bicycle), or along the X-Yplane. In further examples, the shock may be tilted such that it is notfully aligned with either of the X-Y or Y-Z planes. In this example, atleast a portion of the shock would rotate in three-dimensions.

A detailed cross-sectional view of an exemplary pivot joint used in thepivot points 194, 198, 206, 182, 185, 187 is shown in FIG. 8B. In oneexample, each pivot point 194, 198, 206, 182, 185, 187 may include aplurality of rolling-element bearings 252 connected with the first andsecond link assemblies 116, 118 configured to pivot around thecircumference of a respective pivot axle 182. The rolling-elements 252may be generally cylindrically-shaped and may be configured to rollalong respective track surfaces 272. The widths of the track surfaces272 may be slightly larger than the corresponding widths of therolling-element bearings 252, and the distance between track surfaces272 and the surfaces of the pivot axles 182 may be slightly larger thanthe corresponding diameters of the rolling-element bearings 252. Thetrack surfaces 272 may be substantially smooth to provide a low frictionrolling surface for the rolling-elements 252.

As described in more detail below, the rolling-element bearings 252 maybe adapted to roll back and forth along their respective track surfaces272 as the links 117, 119, 127, 129 move in response to displacement ofthe rear wheel 106. More particularly, the rolling-element bearings 252allow the forward link 119 of the first pivot link assembly 116 to pivotwith respect to the front frame 112, and the rear link 117 to pivot withrespect to the swingarm 114 and the forward link 119. Similarly, theforward link 129 of the second pivot link assembly 118 is allowed topivot with respect to the front frame 112 and the rear link 127, and therear link 127 is allowed to pivot with respect to the swingarm 114 andthe forward link 129. Rotation of the links 117, 119 around pivot points194, 198, 206, 182, 185, 187 in response to forces exerted on the rearwheel 106 causes the swing arm 114 to move in an upwards or downwardsdirection relative to the frame 112.

It is to be appreciated that different examples of the presentdisclosure can utilize different roller bearing and track configurationsto provide desired strength and motion characteristics. For example, insome examples, each pivot aperture may define multiple tracks andinclude multiple rolling-element bearings 252 positioned in a parallelorientation. Additionally, other examples may utilize differentconfigurations of rolling-element bearings, including ball bearings,roller bearings, needle bearings, static bearings, and so on.Additionally, while FIG. 8B illustrates a radially centered bearing,other examples may utilize radially off-center bearings.

In the example illustrated in FIGS. 1-14, the forward 117, 127 and rear119, 129 links of the first and second pivot assemblies 116, 118 aresubstantially the same length. Additionally, the links 117, 119, 127,129 of the first and second pivot link assemblies 116, 118 aresubstantially the same length, and the first and second pivot linkassemblies 116, 118 include the same number of pivot points 194, 198,206, 182, 185, 187, i.e., three each. The links can be relatively short,for example, 50 mm for every 100 mm of rear wheel travel. In otherexamples of the link suspension system, the first and second pivot linkassemblies 116, 118 may have any number of pivot points and/or links.For example, the first pivot link assembly 116 may have more or fewerlinks than the second pivot link assembly 118, and may be connected bymore or fewer pivot points. In addition, in other examples, the forwardand rear links of the first and second pivot link assemblies 116, 118may have different lengths, the pivot link assemblies 116, 118 may havedifferent overall or total lengths, or one of the pivot link assembliesmay have more or fewer links than the other. While changing the lengthof the individual links may alter the angular velocity of the links 117,119, 127, 129 as they rotate around the pivot points 194, 198, 206, 182,185, 187, the swing arm 114 and rear wheel 106 will continue to maintaina substantially linear travel path.

FIGS. 9-14 show the rear suspension system 102 in varying stages ofcompression. For example, the rear suspension system 102 may be placedin a partially or fully compressed stage by an upward force applied tothe rear wheel 106 or a downward force applied to the seat 110, such aswhen a rider sits on the bicycle 100, or when the bicycle 100 moves overrough terrain. Such an upward or downward force may activate the shockassembly 120, causing the cylinder body 306 to traverse the length ofthe piston shaft 314 relative to the amount of upward or downward forceexerted on the shock assembly 120. If no force is applied onto the shockassembly 120, it may remain inactive, with the cylinder body 306maintained in an extended position away from the piston shaft 314.

FIGS. 10-11 illustrate the shock assembly 120 in a partially compressedstage. As illustrated, the forward 119, 129 and rear 117, 127 links ofthe first and second link assemblies 116, 118 are in a first elevatedposition. Additionally, the rear pivot points 182, 185 of the firstpivot link assembly 116 and the rear pivot points 194, 198 of the secondpivot link assembly 118 are in a first elevated position with respect tothe bike frame 112. As shown in FIG. 14, a comparison of the compressedstages illustrated in FIGS. 1-9 with FIGS. 10-11 shows that the rearpivot points 182, 185 of the first pivot link assembly 116 and the rearpivot points 194, 198 of the second pivot link assembly 118 have movedupward along the y-axis. The upward movement of the first and secondlink assemblies 116, 118 also forces the cylinder body 306 of the shockassembly 120 upward and onto the piston shaft 314 to place the shockassembly in a partially compressed stage. In addition, as the rearsuspension system 102 moves from the non-compressed stage to thepartially compressed stage, the links 117, 119, 127, 129 may pivotaround the pivot points 194, 198, 206, 182, 185, 187 in a clockwisedirection (as view from the right side of the bicycle).

FIGS. 9, 12-13 illustrate the shock assembly 120 in a fully compressedstage. As illustrated, the forward 119, 129 and rear 117, 127 links ofthe first and second link assemblies 116, 118 are in a second elevatedposition. Additionally, the rear pivot points 182, 185 of the firstpivot link assembly 116 and the rear pivot points 194, 198 of the secondpivot link assembly 118 are in a second elevated position with respectto the bike frame 112. As shown in FIG. 14, a comparison of thecompressed stages illustrated in FIGS. 10-11 with FIGS. 12-13 shows thatthe rear pivot points 182, 185 of the first pivot link assembly 116 andthe rear pivot points 194, 198 of the second pivot link assembly 118have moved upward along the y-axis from the partially compressed stage.The upward movement of the first and second link assemblies 116, 118also forces the cylinder body 306 of the shock assembly 120 furtherupward onto the piston shaft 314 to place the shock assembly in a fullycompressed stage. In addition, as the rear suspension system 102 movesfrom the partially compressed stage to the fully compressed stage, thelinks 117, 119, 127, 129 may pivot around the pivot points 194, 198,206, 182, 185, 187 in a clockwise direction (as view from the right sideof the bicycle). A relatively large upward force applied to the rearwheel 106 or a large downward force applied to the seat 110, such aswhen the rider and the bicycle land on the ground after riding over ajump, can place the rear suspension system in a third fully compressedstage as shown in FIGS. 12-13.

By allowing the rear wheel 106 and the swingarm 114 to move relative tothe front frame 112 through the first and second link assemblies 116,118 as described above, the rear suspension system 102 acts toefficiently absorb forces impacting on the bicycle 100 that can becaused from riding over rough terrain (such as rocks, holes in theground, and the like). As previously mentioned, the shock assembly 120acts to resist displacement of the rear wheel 106 and acts to return therear wheel to its pre-displacement position. In addition, the linkassembly 116, 118 prevents movement of the swingarm 114 along thez-axis, thereby limiting the travel path of the swingarm 114 to asubstantially linear path along the X-Y plane that is substantiallyparallel to the orientation of the shock assembly 120. Accordingly, theswing arm 114 and rear wheel 106 can travel in a substantially linearpath parallel to the y-axis, thereby limiting inefficient use of theshock assembly 120 associated with wheel travel along the x-axis.

A second example of the rear suspension system 402 is shown in FIG. 15.Similar to the first example, the second example of the rear suspensionsystem 402 includes a swingarm 414 coupled with the front frame 412through a link suspension system 415 including a first pivot linkassembly 416, a second pivot link assembly 418, and a shock assembly420, which may be bolted to the front frame 412 and to the swingarm 414.The front frame 412 can include a head tube 422, a top tube 424, a downtube 426, a bottom bracket 428, and a seat tube 430. Additionally, theswingarm 414 includes right and left arms 452, 454 that are connectedtogether by a central attachment member 453 that may also be attached tothe first link assembly 416 and the second link assembly 418. Similar tothe example shown in FIGS. 1-14, the shock 420 may include a pistonshaft 514 and a cylinder body 506.

As will be further discussed below, the central attachment member 453may define right and left link attachment portions 467, 469 to which therear links 417, 427 of the first and second link assemblies 416, 418 arepivotally attached, thereby connecting the swingarm 114 with the downtube 426 of the front frame 412. The central attachment member 453 mayalso include an axle 461 adapted to rotatably receive the bottom end ofthe shock assembly 420 to connect the shock assembly 420 to the centralattachment member 453. The top end of the shock assembly 420 may berotatably connected to the seat tube 430 via an axle 300 mounted on thetop end of the piston shaft 414 and corresponding receiving apertures402 defined by the seat tube 430. As shown in FIG. 15, the shock 420 maybe parallel to the y-axis when mounted to the seat tube 430 and to thecentral attachment member 453.

The link suspension system 415 may include first and second pivot linkassemblies 416, 418 that are positioned in a v-shaped configuration.Accordingly, in contrast to the example shown in FIG. 1, the first andsecond pivot link assemblies 416, 418 are not crossed in position, i.e.,the positions of the first and second pivot link assembles 416, 418 donot overlap or intersect along the z-axis, instead forming a “V.” Thefirst pivot link assembly 416 may include a rear link 417 that ispivotally connected to a forward link 419. The rear end of the rear link417 may be pivotally connected to the right link attachment portion 467of the central attachment member 403, and the front end of the rear link417 may be pivotally connected to the rear end of the forward link 419.Referring to FIG. 15, the front end of the forward link 419 may bepivotally connected to the front frame 412 on the right side of theframe. In particular, the front end of the forward link 419 may bepivotally connected to the triangular shaped mounting portion 520defined by the down tube 426 of the front frame 412.

The second pivot link assembly 418 may be similar in configuration tothe first pivot link assembly 416. For example, the second pivot linkassembly 418 may also include a rear link 427 that is pivotallyconnected to a forward link 429. The rear end of the rear link 427 maybe pivotally connected to the left link attachment portion 469 of thecentral attachment member 403, and the front end of the rear link 427may be pivotally connected to the rear end of the forward link 429.Referring to FIG. 15, the front end of the forward link 429 may bepivotally connected on left side of the front frame 412. In particular,the front end of the forward link 429 may be pivotally connected to thetriangular shaped mounting portion 420 defined by the down tube 426 ofthe front frame 412.

As discussed above, the first and second pivot link assemblies 416, 418may be positioned in v-shaped configuration. More particularly, as shownin FIG. 15, the first pivot link assembly 416 may extend transverselyfrom the right link attachment portion 467 of the central attachmentmember 453 to the right mounting arm 512 of the mounting portion 520 todefine an angle A with respect to the longitudinal axis of the frame,i.e., the x-axis. The first pivot link assembly 146 may benon-orthogonal to the z-axis and the axis of rotation of the rear wheel,which is parallel to the z-axis. The angle A may be between 0 and 90degrees with respect to the longitudinal axis of the frame. In otherexamples, the angle A may be between 90 to 180 degrees, 180 to 270degrees, or 270 to 360 degrees with respect to the longitudinal axis ofthe frame. The axes of rotation of the forward and rear links 417, 419around the pivot points 482, 483, 489 may be orthogonal to theorientation of the links, and may further be non-orthogonal to thelongitudinal axis of the frame 412. More particularly, the axes ofrotation of the links 417, 419 around the pivot points 482, 483, 489 mayform an angle between 0 and 90 degrees with respect to the longitudinalaxis of the frame. In other examples, the axes of rotation, may form anangle between 90 to 180 degrees with respect to the longitudinal axis ofthe frame and to the x-axis, or between 180 to 270 or 270 to 360 degreeswith respect to the longitudinal axis of the frame and to the x-axis.

Similarly, the second pivot link assembly 418 may extend from the leftlink attachment portion 469 of the central attachment member 453 to theleft mounting arm 512 of the mounting portion 520 to define an angle Bwith respect to the longitudinal axis of the frame. The axes of rotationof the forward and rear links 427, 429 around the pivot points 496, 500,508 may be orthogonal to the orientation of the links 427, 429 andnon-parallel to the z-axis. As shown in FIG. 5, the angle B definedbetween the second pivot link assembly 418 and the x-axis may be equalto the angle A defined between the first pivot link assembly 416 and thex-axis, thereby equalizing the distribution of forces along the firstand second pivot link assemblies 418.

The transverse orientation of the link assemblies 416, 418 serves torestrict horizontal movement of the swingarm 414 along the z-axis,thereby preventing side-to-side wobbling of the swingarm 414 and theconnected rear wheel 406. More particularly, the first link assembly 416may provide an opposing force to counterbalance movement of the swingarm414 to the left, while the second link assembly 418 may provide anopposing force to counterbalance movement of the swingarm 414 to theright. Accordingly, the swingarm 414 is prevented from moving back andforth along the z-axis, and instead travels along a travel path locatedalong a plane parallel to the y-plane.

The transverse orientation of the link assemblies 416, 418 furtherconfines any motion of the swingarm 414 and the connected rear wheel 406to a substantially linear path having limited or no curvature. Each ofthe link assemblies 416, 418 acts as a yoke so as to resist loads causedby motion of the swingarm 414. Similar to other examples describedabove, the path traversed by the swingarm 414 may be adjusted bymodifying the angle defined between the shock 420 and the y-axis, andadjusting the mounting positions of the pivot link assemblies 416, 418such that the linear path defined by the assemblies 416, 418 issubstantially parallel to the orientation of the shock 420. In thisconfiguration, the rear wheel 406 can travel in a substantially linearpath, allowing for a 1:1 leverage ratio and maintaining the efficiencyof the shock 420 in absorbing forces exerted on the wheel. If the shock420 is oriented so that it is parallel to the y-axis and the linkassemblies 416, 418 are mounted so that the path defined by the linkassemblies 416, 418 is parallel to the orientation of the shock, thenthe travel path of the swingarm 414 will be confined to a linear paththat is substantially parallel to the y-axis. In other examples, theshock 420 may be tilted rearward or forward to form an angle withrespect to the y-axis and the link assemblies 416, 418 mounted so thatthe path defined by the link assemblies 416, 418 is not parallel to theorientation of the shock. In such examples, the leverage ratio maydeviate from 1:1.

A third example of the rear suspension system 702 is shown in FIGS. 16Aand 16B. The front frame 712 is connected to a swingarm, including arear frame 714 that is coupled with the front frame 712 through a linksuspension system 715. As shown, the rear frame 714 may include rightand left rear triangles 752, 754. Generally, each of the right and lefttriangles 752, 754 includes a forward member 757 connected to a chainstay 759 which extends from the bottom end of the forward member 757 toa rear end portion 756 configured for receiving one end of a rear wheelaxle, and to a seat stay 758 that extends diagonally from the rear endportion 756 of the chain stay 759 to the top end of the forward member757. The rear end portions 756 of the right and left rear triangles 752,754 may be connected, or, in other examples, the rear end portions 756of the right and left rear triangles 752, 754 may be unconnected. It isto be appreciated that the rear frame 714 can be constructed fromvarious types of material, such as aluminum, carbon, titanium, and soon. The members used to construct the rear frame may also define ahollow tubular structure, or may have a solid construction.

Similar to the previously described examples, the link suspension system715 may include a first pivot link assembly 716 and a second pivot linkassembly 718. The first and second pivot link assemblies 716, 718 may becrossed in an X-configuration, as shown. In other examples, the linkassemblies 716, 718 may be arranged in a V-configuration as describedabove. Additionally, the link suspension system 715 includes ahorizontally-oriented shock assembly 725. As is shown, one end of theshock 725 may be coupled to the front frame 712 at fixed pivot point798, and the other end of the shock 725 may be coupled to the rear frameat pivot point 731. In one example, the shock 725 may include a cylinderbody 706, and a piston shaft 720. The piston 720 may be adapted to moveback and forth along the inside length of the cylinder body 706 inresponse to tension and/or compression forces applied to the pistonshaft 720 by the rear frame 714.

The rear frame 714 may be pivotally connected to the front frame 712 viaa swing link 719. The top end of the swing link 719 may define a firstfixed pivot point 728 on the front frame 712 for allowing the swing link719 to pivot relative to the front frame 712. The bottom end of theswing link 719 may define a second pivot point 730 for allowing theswing link 719 to pivot relative to the piston shaft 720 and travelalong an arcuate path about pivot point 728 as the shock 725 iscompressed, thus rotating the shock 725 around pivot point 798.

The rear frame 714 may further be pivotally connected to the front frame719 via the link suspension system 715. More particularly, the rear ends760 of the first and second pivot link assemblies 716, 718 may definerear pivot points 731, 733 for allowing the first and second pivot linkassemblies 716, 718 to pivot relative to the rear frame 714. The frontends 762 of the first and second pivot link assemblies 716, 718 may bepivotally coupled to right and left mounting arms extending from atriangular-shaped mounting portion 200 on the front frame 712 to definefixed front pivot points 737, 739 for allowing the first and secondpivot link assemblies 716, 718 to pivot relative to the down tube 711.In one example, the rear ends 760 of the first and second pivot linkassemblies 716, 718 may each be mounted to a central connection bracket790 positioned between the right and left rear triangles 754, 752forming the rear frame 714. However, in other examples, the first andsecond pivot link assemblies 716, 718 may be directly mounted to thetriangles 754, 752.

FIG. 16B illustrates the rear suspension system 702 of FIG. 16A in anuncompressed stage shown in solid lines, and a partially compressedstage and a fully compressed stage shown in dashed lines. As shown, thesecond rotating pivot point 730 of the swing link 719 may travel alongan arc defined by the distance pivot points 728 and 730 along the lengthof the piston 720 as it is compressed. As the second pivot point 730rotates forward along the length of the piston 720, the first and secondpivot link assemblies 716, 718 may be compressed to guide the rear pivotpoints 731, 733 of the pivot link assemblies 716, 718 in a generallyupward direction toward the front end of the bicycle. Accordingly, thelink suspension system 715 may serve to restrict movement of the rearframe 714 along the z-axis, thereby preventing side-to-side wobbling ofthe rear frame 714 and the connected rear wheel. The link suspensionsystem 715 may thus be configured to function similar to a mechanicalrail or track configured to guide the third and forth pivot points 731,733 between the first pivot point 728 and the down tube 711.

In this configuration, the rear wheel can travel in a substantiallyvertical orientation while utilizing a shorter shock assembly than inthe first and second examples, which include a vertically oriented shockassembly. Accordingly, the leverage ratio may deviate from the 1:1 ratiodiscussed above. Furthermore, the ICC and IC of the rear wheel maymigrate, rather than approach infinity, due to the slightly curved wheeltravel path.

A fourth example of the rear suspension system 1702 is shown in FIGS.17A-17J. Like the example of the rear suspension system 702 shown inFIGS. 16A and 16B, this particular example includes a rear frame 1714that is coupled with the front frame 1712 through a link suspensionsystem 1715. Similar to the rear frame 714 shown and described in FIGS.16A and 16B, the rear frame 1714 may include right and left reartriangles 1752, 1754, each defining a forward member 1757, chain stay759, and a seat stay 1758. The rear end portions of the triangles 1752,1754 being connected by a shaft 1751 configured for receiving the wheelaxle of the rear wheel. However, in other examples, the rear endportions of the right and left rear triangles 1752, 1754 may beunconnected. It is to be appreciated that the rear frame 1714 can beconstructed from various types of material, such as aluminum, carbon,titanium, and so on. The members used to construct the rear frame maydefine a hollow tubular structure, or may have a solid construction.

As described above with respect to other examples, the link suspensionsystem 1715 may include a first pivot link assembly 1716 and a secondpivot link assembly 1718, crossed in an X-configuration, as shown.Additionally, the link suspension system 1715 may further include ahorizontally-oriented shock assembly 1725. The shock 1725 may be coupledbetween the rear frame 1714 and the front frame 1712, and may include acylinder body 1710 and a piston shaft 1720 adapted to move back andforth along the inside length of the cylinder body 1710 in response totension and/or compression forces applied by the rear frame 1714. Asshown, the forward end of the shock 1725 may be pivotally coupled to thedown tube of the front frame 1712, and the rear end of the shock 1725may be pivotally coupled to the rear frame 1714.

Similar to prior examples, the rear ends of the first and second pivotlink assemblies 1716, 1718 may define rear points 1737, 1739 forallowing the first and second pivot link assemblies 1716, 1718 to pivotrelative to the rear frame 1714 and the front ends of the first andsecond pivot link assemblies 1716, 1718 may define front pivot points1731, 1733 for allowing the first and second pivot link assemblies 1716,1718 to pivot relative to the front frame 1712. As discussed above withrespect to other examples, the front ends of the first and second pivotlink assemblies 1716, 1718 may be mounted to a triangular-shapedmounting portion 200 defining right and left mounting arms to which thefirst pivot link assembly 1716 and the second pivot link assembly 1718are pivotally attached. Furthermore, the axes of rotation of the forwardand rear links 1717, 1719, 1727, 1729 may form an angle that is between0 and 90 degrees with respect to the longitudinal axis of the frame 1712(i.e., the x-axis). In other examples, the axes of rotation may form anangle that is between 90 to 180 degrees with respect to the longitudinalaxis of the frame and to the x-axis, or between 180 to 270 or 270 to 360degrees with respect to the longitudinal axis of the frame and to thex-axis.

As best shown in FIG. 17E, which illustrates the rear suspension system1702 with the rear frame 1714 removed, the front ends of the first andsecond pivot link assemblies 1716, 1718 may be pivotally joined to thefront frame, and the rear ends of the first and second pivot linkassemblies 1716, 1718 may be pivotally joined to a mounting bracket 1770at pivot point 1771. A comparison of FIGS. 17F and 17G illustrates thatthe mounting bracket 1770 is configured to travel vertically relative tothe front frame 1712 as the rear frame 1714 is displaced relative to thefront frame 1712. Notably, the mounting bracket 1170 in this particularexample does not physically touch the seat tube 1773 as it travels. Incontrast, the motion of the bracket 1770 is limited by the transverseorientation of the first and second pivot link assemblies 1716, 1718,which confines any motion of the bracket 1770 to a substantially linearpath having limited, if any, curvature. Other examples may includebrackets or other mechanisms that slidably engage the seat tube 1773. Asbest shown in FIGS. 17D, 17F, and 17G, the rear ends of the first andsecond pivot link assemblies 1716, 1718 are configured to both pivotrelative to the bracket 1770 and travel upwardly with the bracket 1770as the shock assembly 1725 is compressed, while the front ends of thefirst and second pivot link assemblies 1716, 1718 are configured topivot relative to the front frame 1712.

Referring back to FIGS. 17A and 17B, the rear frame 1714 may further bepivotally connected front frame 1712 via a swing link 1719. The top endof the swing link 1719 may be pivotally connected to the top tube 1739of the front frame 1712 to define a first pivot point 1728, and thebottom end of the swing link 1719 may be pivotally mounted to the rearframe 1714 to define a second pivot point 1730. As best shown in FIGS.17F and 17G, which illustrate the shock 1725 in fully compressed anduncompressed positions, the swing link 1719 is configured to swingforwardly (i.e., in a counter-clockwise direction) in response tocompression forces applied by the rear frame 1714. The second pivotpoint 1730 may travel along an arcuate path as the swing link 1719swings forwardly, compressing the shock 1725.

The swing link 1719 structure is best illustrated in FIG. 17B. In oneexample, the swing link 1719 may have a dog bone-type structure, inwhich two parallel linkages 1780, 1781, are connected by a horizontalmember 1782 that extends between the linkages 1780, 1781. The linkagesmay be pivotally coupled to the right and left sides of the front frame(i.e., at fixed pivot point 1728), as well as to each of the right andleft triangles 1752, 1754 of the rear frame (i.e., at pivot point 1730).As best shown in FIG. 17B, in one example, the linkages 1780, 1781 arecoupled to the opposing inner surfaces of the top ends of the forwardmembers 1757. However, in other examples, the linkages 1780,1781 may beotherwise coupled to the triangles 1752, 1754. For example, the linkages1780, 1781 may be coupled to the outer surfaces of the forward members1757, along the length of the forward members 1757 (rather than at thetop of the forward members 1757), along the chain stay 1759, or alongthe seat stay 1758.

The rear frame 1714 may further be pivotally connected to the rear endof the piston 1720, which is best shown in FIGS. 17B, 17E, 17F, and 17G.The rear end of the piston 1720 defines an additional pivot point 1799that allows the rear frame 1714 to pivot relative to the shock 1725 andthe front frame 1712. In some examples, such as that shown in FIGS.17A-17J, the rear end of the piston 1720 may be pivotally coupled to amember 1784 connecting the rear triangles 1752, 1754. In other examples,the rear end of the piston 1720 may be pivotally coupled to the swinglink 1719, for example, the piston 1720 may be pivotally coupled to thehorizontal member 1782 or to a separate member extending between thelinkages 1780, 1781. The pivot point 1799 may travel forwardly andupwardly in response to forces impacting upon the rear frame. The topend of the shock 1725 may be pivotally coupled to the front frame 1712at a fixed pivot point 1798 that allows the shock 1725 to pivot relativeto the front frame 1712. Accordingly, and in contrast to some of theother examples previously discussed, the orientation of the shock 1725relative to the front frame 1712 changes as it is compressed.

The rear frame 1714 may further be pivotally coupled to the mountingbracket 1770 that is coupled to the rear ends of the first and secondpivot link assemblies 1716, 1718. As best shown in FIGS. 17F and 17G,forces impacting on the rear frame 1714 may cause the bracket 1770 totravel upwardly with the rear frame 1714 as it is displaced relative tothe front frame 1712.

FIGS. 17C, 17E, 17D, 17F, and 17G illustrate the rear suspension system1702 of FIG. 17A in fully uncompressed and compressed stages. As shown,displacement of the rear wheel causes the rear frame 1714 to travelrelative to the front frame 1712, such that the bracket 1770 is movedupwardly along a substantially linear path. At the same time, the bottomend of the swing link 1719 is rotated in a counterclockwise directiontowards the cylinder body 1710. The rear frame 1714 is further rotatedin a clockwise direction and travels upwardly and forwardly relative tothe front frame 1712. More particularly, the portion of the rear frame1712 coupled to the mounting bracket 1770 is configured to move upwardlyalong the path defined by the bracket 1770, and the portion of the rearframe coupled to the swing link 1719 is configured to move along thearcuate path defined by the bottom end of the swing link 1719. Thistranslation of the rear frame 1714 results in a wheel path that isslightly curved.

FIGS. 17F and 17G illustrate the motion of some of the pivot points1730, 1799, and 1771 of the rear suspension system 1702 shown in FIGS.17A-17J. A comparison of FIGS. 17F and 17G illustrates that rotatingpivot point 1730, which is located at the free end of the swing link1719, travels along an arcuate path around fixed pivot point 1728. Thepath is located a distance away from the fixed pivot point 1728 that issubstantially equal to the distance between the fixed pivot point 1728and the rotating pivot point 1730. The pivot point located at the end ofthe shock 1799 travels along an arcuate path around fixed pivot point1728. In contrast to the pivot point 1730 located on the swing link1719, which maintains a constant distance away from the fixed pivotpoint 1728, the pivot point 1799 located on the shock 1725 moves closerto the fixed pivot point 1728 due to the rotation of the rear frame 1714as it pivots relative to the swing link 1719 and to the shock 1725 as itis compressed. As is also shown in FIGS. 17F and 17G, the pivot point1771 located on the mounting bracket 1770 moves along a linear path thatis defined by the pivot link assemblies 1716, 1718.

Similar to the example rear suspension system shown in FIGS. 16A and16B, the ICC and IC of the rear wheel in this example changes as therear wheel is displaced, resulting in the curved wheel path describedabove. The curvature of the wheel path can be adjusted according todifferent examples by changing the location, geometrical shape of theswing link 1719 and/or the position of the link suspension system 1715.For example, the wheel path may be altered by varying the locations atwhich the front and rear ends of the first and second pivot linkassemblies 1716, 1718 or the swing link 1719 are mounted or changing thelengths of the first and second pivot link assemblies 1716, 1718. Theshock rate can be changed by moving the mounting points at which theends of the shock are mounted to the front and rear frames 1712, 1714.

FIG. 17H illustrates a top down view of the example of the rearsuspension system shown in FIGS. 17A-17G, and 17I and 17J illustratecross-sectional views taken along lines 171-171 and 17J-17J of FIG. 17H.As shown in these figures, the forward and rear links 1717, 1709, 1727,1729 of the first and second pivot link assemblies 1716, 1718 defineangles, A and B, that are substantially equal to one another. While theangles A and B defined by the links 1717, 1709, 1727, 1729 change as theshock 1725 is compressed, the angle B defined by the forward and rearlinks 1717, 1709 of the first pivot link assembly 1716 remainssubstantially equal to the angle A defined by forward and rear links1727, 1729 of the second pivot link assembly 1718 as the shock 1725 iscompressed.

Another example of a rear suspension system 1802 is shown in FIGS.18A-18F. Similar to the example shown in FIGS. 17A-17J, this exampleillustrates a link suspension system 1815 including first and secondpivot link assemblies 1816, 1818 coupled to a mounting bracket 1870 thatis configured to travel vertically relative to the front frame 1812 asthe rear frame 1814 is displaced relative to the front frame 1812. Likethe example shown in FIGS. 17A-17J, the rear frame 1814 is pivotallycoupled to the bracket 1870, and to a rocker link 1819 that joins therear frame 1814 to the front frame 1812. In contrast to the exampleshown in FIGS. 17A-17J, however, the rocker link 1819 coupling the frontand rear frames 1812, 1814 extends upwardly, rather than downwardly,from a fixed pivot point 1828 at the bottom end of the link 1819 to arotating pivot point 1830 at the top end of the link 1819.

Similar to prior examples, the rear ends of the first and second pivotlink assemblies 1816, 1818 may define rear points 1837, 1839 forallowing the first and second pivot link assemblies 1816, 1818 to pivotrelative to the rear frame 1814 and the front ends of the first andsecond pivot link assemblies 1816, 1818 may define front pivot points1831, 1833 for allowing the first and second pivot link assemblies 1816,1818 to pivot relative to the front frame 1812. As discussed above withrespect to other examples, the front ends of the first and second pivotlink assemblies 1816, 1818 may be mounted to a mounting portion 300located along the down tube 1805 defining right and left mounting armsto which the first pivot link assembly 1816 and the second pivot linkassembly 1818 are pivotally attached. Furthermore, the axes of rotationof the forward and rear links 1817, 1819, 1827, 1829 may form an anglethat is between 0 and 90 degrees with respect to the longitudinal axisof the frame 1712 (i.e., the x-axis). In other examples, the axes ofrotation may form an angle that is between 90 to 180 degrees withrespect to the longitudinal axis of the frame and to the x-axis, orbetween 180 to 270 or 270 to 360 degrees with respect to thelongitudinal axis of the frame and to the x-axis.

Similar to the example shown in FIGS. 17A-17J, the rocker link 1819 mayhave a dog bone-type structure, in which two parallel linkages 1880,1881 are connected by a horizontal member 1882, that extends between thelinkages 1880, 1881. The bottom ends of the linkages 1880, 1881 may bepivotally coupled to the right and left sides of the mounting portion300 of the front frame 1812 (i.e., at fixed pivot point 1828). The topends of the linkages 1880, 1881 may be pivotally coupled to the top endsof the front members 1857 of the right and left triangles 1852, 1854 ofthe rear frame (i.e., at pivot point 1830), as well as to the rear endof the shock assembly 1825 at pivot point 1830. As best shown in FIG.18B, in one example, the top ends of the linkages 1880, 1881 are coupledto the opposing inner surfaces of the forward members 1757. However, inother examples, the linkages 1880,1881 may be otherwise coupled to thetriangles 1852, 1854. For example, the linkages 1880, 1881 may becoupled to the outer surfaces of the forward members 1857, along thelength of the forward members 1857 (rather than at the top of theforward members 1857), along the chain stay 1859, or along the seat stay1858.

As discussed above, the rear end of the shock assembly 1825 may bepivotally coupled to the front members 1857 of the triangles 1852, 1854,and to the top end of the rocker link 1819 at pivot point 1830. Similarto the example shown in FIGS. 17A-17J, the top end of the shock assembly1825 may be pivotally coupled to the front frame at fixed pivot point1898.

As mentioned above, and as best shown in FIGS. 18C, 18D, 18F, and 18G,compression of the shock 1825 in response to tension and/or compressionforces applied by the rear frame 1814 causes the bracket 1870 to travelalong a substantially linear vertical path as described above withrespect to the example shown in FIGS. 17A-17J. At the same time, the topend of the link 1819, which is pivotally coupled to the bottom end ofthe shock 1825 and to the rear frame 1814, travels along an arcuate pathas the link 1819 is rotated in a clockwise direction towards thecylinder body 1810.

The shock 1825 is also configured to pivot in relative to the frontframe as the bottom end of the shock 1825 is moved along the arcuatepath defined by the link 1819. At the same time, the portion of the rearframe 1814 coupled to the mounting bracket 1870 is configured to moveupwardly along the linear path defined by the bracket 1870, and theportion of the rear frame 1812 coupled to the top end of the rocker link1819 is configured to move along the arcuate path defined by the rockerlink 1819, resulting in a wheel path that is slightly curved.

FIGS. 18F and 18G illustrate the motion of some of the pivot points 1830and 1871 of the rear suspension system 1802 shown in FIGS. 18A-18G. Acomparison of FIGS. 18F and 18G illustrates that pivot point 1830, whichis located at the free end of the rocker link 1819, travels along anarcuate path around fixed pivot point 1828. The path is located adistance away from the fixed pivot point 1828 that is substantiallyequal to the distance between the fixed pivot point 1828 and the pivotpoint 1830. The end of the shock 1825, which is pivotally coupled to therear frame 1814 and to the rocker link 1819 at pivot point 1830, alsotravels along this same arcuate path. As is also shown in FIGS. 18F and18G, pivot point 1871, which is defined between the mounting bracket1870 and the rear frame 1814, travels along a linear path that isdefined by the pivot link assemblies 1816, 1818.

Another example of a rear suspension system is shown in FIGS. 19A-19G.This example is similar to the one shown in FIGS. 18A-18G in that thefront and rear frames 1912, 1914 are coupled via a rocker link 1919.Similar to other examples, the rocker link 1919 may have a dog bone-typestructure, in which two parallel linkages 1980, 1981 are connected by ahorizontal member 1982 that extends between the linkages 1980, 1981.

In contrast to the example shown in FIGS. 18A-18G, however, thepositions of the rocker link 1919 and the first and second pivot linkassemblies 1916, 1918 are reversed. More particularly, the ends of thepivot link assemblies 1916, 1918 are pivotally coupled to the down tube1905 and to a mounting bracket 1906 that is pivotally coupled to therear end of the shock assembly 1925. As will be further discussed below,the mounting bracket 1906 is further coupled to the rear ends of thefirst and second pivot link assemblies 1916, 1918 and travels along asubstantially linear path defined by the first and second pivot linkassemblies 1916, 1918 as the shock 1925 is compressed. The top free endof the rocker link 1919 is pivotally coupled to the down tube 1905 atpivot point 1930, and the fixed end of the rocker link 1919 is pivotallycoupled to the rear frame 1914 at pivot point 1928. In other examples,the pivot link assemblies 1916, 1918 may be directly joined to the rearend of the shock assembly 1925, rather than the mounting bracket 1906.

As best shown in FIG. 19B, the mounting bracket 1906 defines two angledmounting arms 1936, 1937 to which the rear ends of the first and secondpivot link assemblies 1916, 1918 are pivotally attached. As discussedabove with respect to other examples, the axes of rotation of theforward and rear links 1917, 1919, 1927, 1929 may form an angle that isbetween 0 and 90 degrees with respect to the longitudinal axis of thefront frame 1912 (i.e., the x-axis). In other examples, the axes ofrotation may form an angle that is between 90 to 180 degrees withrespect to the longitudinal axis of the frame and to the x-axis, orbetween 180 to 270 or 270 to 360 degrees with respect to thelongitudinal axis of the frame and to the x-axis.

The mounting bracket 1906 may further define a slot 1933 configured toreceive the rear end of the shock 1925, which may be pivotally attachedto an axle 1938 that extends through the slot in a directionperpendicular to the longitudinal axis of the front frame 1912. The axisof rotation of the shock 1925 around the axle 1938 is illustrated on themounting bracket 1906 as pivot point 1999. The mounting bracket 1906,which is pivotally coupled to each of the pivot link assemblies 1916,1918, the shock 1925, and the front members 1957 of the rear frame 1914,thus functions similar to a small link system that interconnects thesecomponents and further guides the motion of the rear frame 1914.

Similar to other examples, the rear frame 1914 may include right andleft triangles 1952, 1954 each defining a front member 1957, seat stay1958, and chain stay 1959. The top ends of the front members 1957 may bepivotally attached to the mounting bracket 1906 at pivot point 1931, andthe bottom ends of the front members 1957 may be pivotally attached tothe top end of the rocker link at pivot point 1930.

As best shown in FIGS. 19C, 19D 19F, and 19G, compression of the shock1925 in response to tension and/or compression forces applied by therear frame 1914 causes the rocker link 1919 to rotate in a clockwisedirection, such that the portion of the rear frame 1914 coupled to thelink 1919 rotates upwardly along an arcuate path defined by the top endof the rocker link 1919. As discussed above, the rear frame 1914 isfurther coupled to the mounting bracket 1906, which, in turn, is coupledto the pivot link assemblies 1916, 1918 and to the rear end of the shock1925. In this example, the transverse orientation of the link assemblies1916, 1918 serves to confine any motion of the mounting bracket 1906 andthe attached piston shaft 1920 to a substantially linear path havinglimited, if any, curvature. Additionally, in the illustrated embodiment,the shock 1925 is oriented such that it is substantially parallel to thelinear path defined by the link assemblies 1916, 1918. Since the pistonshaft 1920 is being pushed into the cylinder body 1910 along a path thatis substantially parallel to the linear path defined by the pivot linkassemblies 1916, 1918, the orientation of the shock 1925 only changesminimally, if at all, relative to the front frame 1914 as the shock 1925is compressed and uncompressed.

In other examples, the shock may be directly coupled to the rear frame1914 and to the pivot link assemblies 1916, 1918, rather to the mountingbracket 1906. Additionally, in other examples, the shock 1925 may beoriented at an angle with respect to the linear path defined by thepivot link assemblies 1916, 1918.

FIGS. 19F and 19G illustrate the motion of some of the pivot points1931, 1999, and 1930 of the rear suspension system 1902 shown in FIGS.19A-19G. A comparison of FIGS. 19F and 19G illustrates that pivot point1930, which is located at the free end of the rocker link 1919, travelsalong an arcuate path around fixed pivot point 1928. The path is locateda distance away from the fixed pivot point 1928 that is substantiallyequal to the distance between the fixed pivot point 1928 and the pivotpoint 1930. In contrast, the pivot point 1999 between the mountingbracket 1906 and the end of the shock 1925 and the pivot point 1931between the mounting bracket 1906 and the rear frame 1914 travel along alinear path that is defined by the pivot link assemblies 1916, 1918.

In another example, illustrated in FIGS. 20A-20G, the swing link 2019may be attached to the front frame such that it rotates in acounterclockwise, rather than a clockwise direction. This example issubstantially similar to the example shown in FIGS. 19A-19G, but itincludes a swing link 2019 that is fixedly and pivotally attached at oneend to the seat tube 2073 of the front frame 2012. As shown in FIGS.20A-20G, the free end of the swing link 2019 is pivotally coupled to thefront members 2027 of the front members 2057 of the right and left reartriangles 2052, 2054, and rotates along an arcuate path in response totension and/or compression forces applied by the rear frame 2014.

Similar to the example shown in FIGS. 19A-19G, the example shown inFIGS. 20A-20G also utilizes a mounting bracket 2006 that serves tointerconnect each of the pivot link assemblies 2016, 2018, the shock2025, and the front members 2057 of the rear frame 2014, and guide themotion of the rear frame 2014. As best shown in FIG. 20B, the bracket2006 defines two angled mounting arms 2036, 2037 to which the rear endsof the first and second pivot link assemblies 2016, 2018 are pivotallyattached. The mounting bracket 1906 may further define a slot 2033configured to receive the rear end of the shock 2025, which may bepivotally attached to an axle 2038 that extends through the slot 2033 ina direction perpendicular to the longitudinal axis of the front frame2012. The axis of rotation of the shock 2025 around the axle 2038 isillustrated on the mounting bracket 2006 as pivot point 2099.

As best shown in FIGS. 20C, 20D, 20F, and 20G compression of the shock2025 in response to tension and/or compression forces applied by therear frame 2014 causes the swing link 2019 to rotate in acounterclockwise direction, such that the end of the link 2019 coupledto the rear frame 2014 travels upwardly with the rear frame 2014.Similar to the example shown in FIGS. 19A-19G, the rear frame 2014 isfurther coupled to a mounting bracket 2006 which, in turn, is coupled tothe rear end of the shock 2025 and to the free ends of the first andsecond pivot link assemblies 2016, 2018, which serve to confine themotion of the mounting bracket 2006 and the attached piston shaft 2020to a substantially linear travel path. As the shock is compressed, theportion of the rear frame 2014 attached to the free end of the link 2019is configured to travel upwardly along the arcuate path defined by thelink 2014, and the portion of the rear frame 2014 coupled to themounting bracket 2006 is configured to travel along the linear pathdefined by first and second pivot link assemblies 2016, 2018. The motionof the rear frame 2014 is best illustrated in FIGS. 20F and 20G.

FIGS. 20F and 20G illustrate the motion of some of the pivot points2031, 2099, and 2030 of the rear suspension system 2002 shown in FIGS.20A- 20G. A comparison of FIGS. 20F and 20G illustrates that pivot point2030, which is located at the free end of the swing link 2019, rotatesalong an arcuate path around fixed pivot point 2028. The path is locateda distance away from the fixed pivot point 2028 that is substantiallyequal to the distance between the fixed pivot point 2028 and the pivotpoint 2030. In contrast, the pivot point 2099 between the mountingbracket 2006 and the end of the shock 2025 and the pivot point 2031between the mounting bracket 2006 and the rear frame 2014 both travelalong a linear path that is defined by the pivot link assemblies 2016,2018.

Another example of the rear suspension system 802 is shown in FIGS. 21Aand 21B. As shown in FIG. 21A, the fourth example may include a swingarm814 coupled with the front frame 712 through a link suspension system815 including a first pivot link assembly 816, a second pivot linkassembly 818, and a shock assembly 820, which may be pivotally attachedbetween the front frame 812 and the swingarm 814. Similar to the exampleshown in FIG. 15, this example may include first and second pivot linkassemblies 816, 818 that are positioned in a v-shaped configuration.Accordingly, in this example, the pivot link assemblies 816, 818 are notcrossed, and instead extend at angles away from the longitudinal axis ofthe frame 814.

As shown in FIG. 21A, the first and second pivot link assemblies 816,818 may not have to be the same length. For example, the first pivotlink assembly 816 may have a longer or shorter overall length than thesecond pivot link assembly 818. In one example, the forward link 817 ofthe first pivot link assembly 816 may be longer or shorter than theforward link 827 of the second pivot link assembly 818, and the rearlink 819 of the first pivot link assembly 816 may be longer or shorterthan the rear link 829 of the second pivot link assembly 818. In otherexamples, the forward and rear links 817, 819 of the first pivot linkassembly 816 may have different lengths, and the forward and rear links827, 829 of the second pivot link assembly 818 may have differentlengths. Similar to other examples, the forward ends of the pivot linkassemblies 816, 818 may be pivotally coupled to right and left mountingarms 860, 862 which extend at angles from a triangular-shaped mountingportion 800 of the front frame 812. The rear ends of the pivot linkassemblies 816, 818 may be attached to angled mounting surfaces definedon a mounting portion 813 located at the front end of the swingarm 814.Furthermore, the axes of rotation of the forward and rear links 817,819, 827, 829 define an angle that is between 0 and 90 degrees withrespect to the longitudinal axis of the frame 812 (i.e., the x-axis). Inother examples, axes of rotation may form an angle that is between 90 to180 degrees with respect to the longitudinal axis of the frame and tothe x-axis, or between 180 to 270 or 270 to 360 degrees with respect tothe longitudinal axis of the frame and to the x-axis.

The pivot points of the first and second pivot link assemblies 816, 818also may not be aligned along any particular axis. As best shown in FIG.21B, for example, the front pivot point 852 of the second pivot linkassembly 818 and the front pivot point 850 of the first pivot linkassembly 816 may be positioned at different points along the x-axis sothat the front pivot point 852 of the second pivot link assembly 818 ispositioned in front of (or behind) the front pivot point 850 of thefirst pivot link assembly 816. Similarly, as best shown in FIG. 21A, thefront pivot point 852 of the second pivot link assembly 818 and thefront pivot point 850 of the first pivot link assembly 816 may bepositioned at different points along the y-axis so that the front pivotpoint 852 of the second pivot link assembly 818 is positioned above (orbelow) the front pivot point 850 of the first pivot link assembly 816.In other examples, the rear and central pivot points of the first andsecond pivot link assemblies 816, 818 may be similarly offset.

To maintain a substantially vertical rear wheel travel path, the angle Aformed between the second pivot link assembly 818 and the front frame812 may be substantially equal to the angle B formed between the firstpivot link assembly 816 and the frame 812. This may serve to preventside-to-side wobbling of the swingarm 814 along the z-axis, even whenthe link assemblies 816, 818 are not the same length, or when the linkassemblies 816, 818 are positioned in front of or behind one another.

Another example of the rear suspension system 902 is shown in FIGS. 22Aand 22B. As shown in FIG. 22A, this example may include a swingarm 914coupled with the front frame 912 through a link suspension system 915including a first pivot link assembly 916, a second pivot link assembly918, and a shock assembly 920, which may be pivotally coupled betweenthe front frame 912 and the swingarm 914. Similar to the example shownin FIG. 15 and to the example shown in FIGS. 21A and 21B, the first andsecond pivot link assemblies 916, 918 may be uncrossed.

Both the front pivot points 950, 952 and rear pivot points 954, 956 ofthe first and second pivot link assemblies 916, 918 may be verticallyoffset from one another so that the first and second pivot linkassemblies 916, 918 do cross or overlap along the y-axis. For example,as shown in FIG. 22A, the front pivot point 952 of the second pivot linkassembly 918 and the front pivot point 950 of the first pivot linkassembly 916 may be positioned at different points along the y-axis sothat the front pivot point 952 of the second pivot link assembly 918 ispositioned above (or below) the front pivot point 950 of the first pivotlink assembly 916. Similarly, the rear pivot point 956 of the secondpivot link assembly 918 and the rear pivot point 954 of the first pivotlink assembly 916 may be positioned at different points along the y-axisso that the rear pivot point 956 of the second pivot link assembly 918is positioned above (or below) the rear pivot point 954 of the firstpivot link assembly 916.

Referring to FIG. 22B, the angle A formed between the second pivot linkassembly 918 and the front frame 912 may be substantially equal to theangle B formed between the first pivot link assembly 916 and the frame912. This may serve to maintain a substantially vertical rear wheeltravel path, while preventing side-to-side wobbling of the swingarm 914along the z-axis, even when the first and second pivot link assemblies916, 918 are vertically offset. Similar to other examples, the forwardends of the pivot link assemblies 916, 918 may be pivotally coupled toright and left mounting arms 960, 962 which extend at angles from atriangular-shaped mounting portion 900 of the front frame 912. The rearends of the pivot link assemblies 916, 918 may be attached to angledmounting surfaces defined on a mounting portion 913 located at the frontend of the swingarm 914. Furthermore, the axes of rotation of theforward and rear links 917, 919, 927, 929 may form an angle that isbetween 0 and 90 degrees with respect to the longitudinal axis of theframe 912 (i.e., the x-axis). In other examples, the axes of rotationmay form an angle that is between 90 to 180 degrees with respect to thelongitudinal axis of the frame and to the x-axis, or between 180 to 270or 270 to 360 degrees with respect to the longitudinal axis of the frameand to the x-axis.

Another example of the rear suspension system 2202 is shown in FIGS.23A-230. In this example, the top and bottom ends of a floating shockassembly 2225 may be attached between the first and second pivot linkassemblies 2216, 2218 of a link suspension system 2215. As shown inFIGS. 23A-230, this example may include a swingarm 2214 coupled with thefront frame 2212 through a link suspension system 2215 including a firstpivot link assembly 2216, a second pivot link assembly 2218, and afloating shock assembly 2225. The top end of the floating shock assembly2225 (i.e., the top end of the cylinder 2210) is joined to the firstpivot link assembly 2216 and the bottom end of the floating shockassembly 2225 (i.e., the bottom end of the piston shaft 2220) is joinedto the second pivot link assembly 2218. As shown in this particularexample, the top end of the floating shock assembly 2225 is joined tothe forward link 2217 of the first pivot link assembly 2216, and thebottom end of the floating shock assembly 2225 is joined to the rearlink 2229 of the second pivot link assembly 2218. Both the top andbottom ends of the floating shock assembly 2225 are configured to movewith the links 2217, 2219, 2227, 2229 of the first and second pivot linkassemblies 2216, 2218 to which they are joined as the floating shock2225 is compressed. In other words, the top end of the floating shock2225 is configured to move along a path defined by the forward link 2217of the first pivot link assembly 2216, and the bottom end of thefloating shock 2225 is configured to move along a path defined by therear link 2229 of the second pivot link assembly 2218. Similar to otherexamples, the forward and rear links 2217, 2219, 2229, 2227 of the firstand second pivot link assemblies 2216, 2218 are further configured topivot relative to one another around pivot points 2291, 2294 definedbetween the links 2217, 2219, 2229, 2227.

The pivot link assemblies 2216, 2218 extend at angles from mountingportions 2200 defined by the top and down tubes of the front frame 912.In one example, each mounting portion 2200 may define a mounting arm2201, 2203 to which the forward ends of the link assemblies 2216, 2218are pivotally coupled. The rear ends of the pivot link assemblies 2216,2218 may be attached to angled mounting surfaces defined on the top andbottom ends of the forward member 2257 of the rear frame 2214. As shownin FIG. 23A, the rear frame 2214 may define right and left triangles2252, 2254 that extend rearwardly at angles away from the forward member2257.

Similar to other embodiments, the axes of rotation or pivot points 2290,2291, 2292, 2293, 2294, 2295 of the forward and rear links 2217, 2219,2227, 2229 may form an angle that is between 0 and 90 degrees withrespect to the longitudinal axis of the frame 2212 (i.e., the x-axis).As previously discussed with respect to FIG. 5, each link assembly 2216,2218 defines a plane that defines an angle relative to and intersectsthe longitudinal axis of the front frame 2212. The top and bottom endsof the floating shock 2225, which are joined to the links 2217, 2219,2229, 2227 also move along respective travel paths that are parallel tothe planes defined by the pivot link assemblies 2216, 2217, with the topand bottom ends moving along different planar paths. With respect to theexample shown in FIGS. 23A-23O, the top end of the shock travels along aplane parallel to the plane defined by the first pivot link assembly2316, and the bottom end of the shock travels along a plane parallel tothe plane defined by the second pivot link assembly 2318, whichintersects the plane defined by the first pivot link assembly 2316.Accordingly, the body of the shock 2225 (i.e., the piston shaft 2020 andcylinder body 2010), as well as its longitudinal axis, travels in athree-dimensional motion due to the simultaneous motion of the top andbottom ends along intersecting planes as the shock 2225 is compressed.

As will be further described below, the top and bottom ends of thefloating shock 2225 travel in each of the x, y, and z directions, as theshock is compressed. Notably, despite the travel of the ends of thefloating shock assembly 2225 along the x, y, an z axes, the motion ofthe swing arm 2214 and corresponding wheel travel path are substantiallyconfined to the X-Y plane due to the transverse orientation of the linkassemblies 2216, 2218.

In other examples, the ends of the floating shock assembly 2225 may beotherwise attached to the links of the first and second pivot linkassemblies 2216, 2218 to generate different wheel paths. For example,the top end of the floating shock assembly 2225 may be joined to therear link 2219 of the first pivot link assembly 2216 and the bottom endof the floating shock assembly 2225 may be joined to the forward link2227 of the second pivot link assembly 2218. In a further example, thetop and bottom ends of the floating shock 2225 may be coupled to thefront links 2217, 2227 or the rear links 2219, 2229 of the first andsecond pivot link assemblies 2216, 2218. In the illustrated example, theends of the floating shock assembly 2225 are joined to the links 2217,2227, 2219, 2229 via heim joints, although other examples may utilizedifferent types of joints, such as multi-orientation joints, for joiningthe floating shock assembly 2225 to the links.

In contrast to other examples described herein, the floating shock 2225of the example shown in FIGS. 23A-230 is configured to travel in threedimensions due to the crossed configuration of the first and secondpivot link assemblies 2216, 2218. The motion of the floating shock 2225is best illustrated in FIGS. 23E-230, which show various views of therear suspension system 2002 along different planes of travel,demonstrating that the top and bottom ends of the floating shock areconfigured to move along each of the x, y, and z axes as the shock iscompressed, and that the shock 2225 changes orientation relative to thefront frame 2212 as it is compressed. For example, FIG. 23E-23Gillustrate show various front views of the floating shock 2225 and pivotlink assemblies 2216, 2218 in fully compressed and uncompressed states.Specifically, FIG. 23E illustrates the floating shock 2225 in anuncompressed state, FIG. 23F illustrates the floating shock in a fullycompressed state, and FIG. 23G illustrates the shock 2225 in both anuncompressed state in solid lines and in a compressed state in dashedlines. Additionally, FIG. 230 illustrates a rear view of the floatingshock in both an uncompressed state (in solid lines) and a partiallystate (in dashed lines) with the pivot link assemblies 2216, 2218removed. These figures serve to illustrate the movement of the ends ofthe shock 2225 along the Y-Z plane. Comparing the positions of the topand bottom ends of the shock 2225 in the fully compressed anduncompressed states, the top end of the shock 2225, which is attached tothe forward link 2217 of the first pivot link assembly 2216 moves bothupwardly along the y-axis and towards the left-hand side of the bicyclealong the z-axis. The bottom end of the shock 2225, which is attached tothe rear link 2229 of the second pivot link assembly 2219, moves bothupwardly along the y-axis, as well as towards the left-hand side of thebicycle along the z-axis.

FIGS. 23H-23J illustrate top views of the swing arm 2214, floating shock2225, and pivot link assemblies 2216, 2218. Specifically, FIG. 23Jillustrates the floating shock 2225 in an uncompressed state, FIG. 23Iillustrates the floating shock in a fully compressed state, and FIG. 23Hillustrates the shock 2225 in both an uncompressed state in solid linesand in a compressed state in dashed lines. FIG. 23M illustrates a topview of the floating shock in both the compressed and uncompressedstates (in dashed lines) with the pivot link assemblies 2216, 2218removed. These figures serve to illustrate the movement of the ends ofthe shock 2225 along the X-Z plane. As is shown, the top end of theshock 2225, which is attached to the forward link 2217 of the firstpivot link assembly 2216 moves both rearwardly along the x-axis andslightly towards the left-hand side of the bicycle along the z-axis. Thebottom end of the shock 2225, which is attached to the rear link 2229 ofthe second pivot link assembly 2219, moves forwardly along the x-axis,as well as towards the left-hand side of the bicycle along the z-axis.

FIGS. 23K-23L illustrate side views of the swing arm 2214, floatingshock 2225, and pivot link assemblies 2216, 2218. Specifically, FIG. 23Killustrates the floating shock 2225 in an uncompressed state, and FIG.23L illustrates the floating shock in a partially compressed state. FIG.23N further illustrates a rear view of the floating shock in both thecompressed and partially compressed states (in dashed lines) with thepivot link assemblies 2216, 2218 removed. These figures serve toillustrate the movement of the ends of the shock 2225 along the X-Yplane as the shock moves from a fully compressed to a partiallycompressed state. As is shown, the top end of the shock 2225, which isattached to the forward link 2217 of the first pivot link assembly 2216moves both rearwardly along the x-axis and upwardly along the y-axis.The bottom end of the shock 2225, which is attached to the rear link2229 of the second pivot link assembly 2219, also moves upwardly alongthe y-axis and slightly rearwardly along the x-axis.

In other examples, the curve defined by the instantaneous leverageratios as the floating shock is compressed can be varied by changing theposition and length of the link assemblies, as well as the attachmentpoints of the floating shock assembly. Accordingly, this example may beparticularly well-suited for use in conjunction with commercialoff-the-shelf shock assemblies, since the attachment points of the shockassemblies on the links may be easily and relatively inexpensivelyadjusted to allow for the creation of different leverage ratios. In someother examples, the first and second pivot link assemblies 2216, 2218may be oriented in a V-configuration, rather than crossed.

FIGS. 24A-24G illustrate another example of a rear suspension system2502 for a bicycle. Similar to prior embodiments, this example includesa front frame 2512 operably associated with a rear frame 2514, a shock2525, a dog bone link 2519, and a link suspension system 2515 includingfirst and second pivot link assemblies 2516, 2518 arranged in a crossedconfiguration.

As best shown in FIG. 25, which illustrates the components of the frontframe 2512 with the rear frame 2514 removed, the forward end of theshock 2525 may be pivotally coupled to the down tube 2505 of the frontframe 2512 at a fixed pivot point 2598. The rear end of the shock 2512may be pivotally coupled to the top end of the dog bone link 2519 atrotating pivot point 2599. The bottom end of the dog bone link 2519 maybe pivotally coupled to the seat tube 2503 of the front frame 2512 atfixed pivot point 2592. Specifically, the dog bone link 2519 may becoupled to the front frame 2512 at a protrusion that extends from theseat tube 2503 towards the forward end of the bicycle. The rear frame2514 may also be pivotally coupled to the dog bone link 2519 at a pivotpoint 2591, which is located between the top and bottom ends of the dogbone link 2519. As the dog bone link 2519 rotates about fixed pivotpoint 2592, it causes rotation of the top end of the front member 2572of the rear frame 2514 along an arcuate path defined by the link 2519.

The forward ends of the first and second pivot link assemblies 2516,2518 of the link suspension system 2515 may be pivotally coupled tomounting portion 2500 that extends from the down tube 2505 of the frontframe 2512. The rear ends of the pivot link assemblies 2516, 2518 may becoupled to a mounting bracket 2570 that is, in turn, pivotally coupledto the rear frame 2514 at pivot point 2571. As with some of the examplespreviously described, the mounting bracket 2570 may be configured totravel along a substantially linear path defined by the transverseorientation of the pivot link assemblies 2516.

FIGS. 24A-24D, 24G, and 24H illustrate the relative motion of the shock2525, link 2519, pivot link assemblies 2516, 2518, and rear frame 2514relative to the front frame 2512 as the shock 2525 is compressed.Specifically, FIG. 24A illustrates the rear suspension system 2502 whenthe shock 2525 in an uncompressed state, FIG. 24B illustrates the rearsuspension system 2502 when the shock 2525 is in a partially compressedstate, and FIG. 24C illustrates the rear suspension system 2502 when theshock 2525 is in a fully compressed state. FIG. 24D illustrates acomparison of the three states shown in FIGS. 24A-24C, with the shock2525 shown in the uncompressed state in solid lines, as well as in thepartially and fully compressed state in dashed lines. FIG. 24Eillustrates a magnified view of the mounting bracket in FIG. 24D. Acomparison of FIGS. 24A-24B illustrates that partial compression of theshock 2525 causes the dog bone link 2519 to pivot in a clockwisedirection around fixed pivot point 2592. The pivot point 2599 located atthe top end of the link 2519, and the pivot point 2591 located along thelength of the link 2519 are configured to move along arcuate pathsdefined by the rotation of the link 2519 around the fixed pivot point2592. The rear end of the shock 2525, and the top end of the reartriangle 2514, which are coupled to the link at the pivot points 2599,2591, are also configured to move along the arcuate paths defined by thepivot points 2599, 2591. At the same time, the mounting bracket 2571 isconfigured to travel in a rearward direction, such that the pivot point2571 defined between the bracket 2570 and the rear frame 2514 travelsbackwardly along the linear path defined by the pivot link assemblies2516.

A comparison of FIGS. 25B and 25C illustrates that further compressionof the shock 2525 causes the dog bone link 2519 to rotate further in aclockwise direction around pivot point 2592, such that the shock 2525 isalso rotated around fixed pivot point 2598. Additionally, the mountingbracket 2570 is configured to switch directions, such that the pivotpoint 2571 defined between the bracket 2570 and the rear frame 2514travels forwardly along the linear path defined by the pivot linkassemblies 2516, 2518.

As discussed above, the mounting bracket 2570 may be configured totravel in both backwards and forwards directions along the substantiallylinear path defined by the pivot link assemblies 2516, 2518 as the shock2525 transforms between the uncompressed and fully compressed states. Inother words, the mounting bracket 2570 and the attached portion of therear frame 2514 are configured to move both backwards and forwards alongthe linear path as the rear wheel travels along the full wheel pathduring one of compression or extension of the shock. The back and forthmotion of the bracket 2570 and rear frame 2514 are best shown in FIGS.24D and 24E. As the rear wheel moves upwardly along the wheel path, thebracket 2570 initially moves rearwardly along the linear path defined bythe pivot link assemblies 2516, 2518. At the same time, the top end ofthe rear frame 2514 travels forwardly along the arcuate path defined bythe link 2519, resulting in a wheel path that is increasingly curved orconcave (i.e., the radius of curvature of the wheel path decreases asthe rear wheel travels upwardly). Once the rear wheel hits an inflectionpoint along the wheel path, or the point at which the curvature orconcavity of the wheel path changes sign, the bracket 2570 switchesdirections such that it begins to travel in the opposite direction (inthis case, forwardly) along the linear path defined by the pivot linkassemblies 2516, 2518. Accordingly, the bracket 2570 and the attachedportion of the rear frame 2514 are configured to move rearwardly andforwardly along the linear path defined by the pivot link assemblies2516, 2518 during each compression or extension of the shock 2525. Inother embodiments, the mounting points and configurations of the link2519, shock, 2525, and pivot link assemblies 2516, 2518 may be adjustedso that the bracket 2570 moves forwardly first, and then rearwardlyalong the linear path.

FIGS. 24G and 24H illustrate the motion of pivot points 2599, 2591, and2571 as the shock 2525 is compressed. A comparison of FIGS. 20G and 20Hillustrates that pivot point 2099, which is located at the free end ofthe dog bone link 2519, rotates along an arcuate path around fixed pivotpoint 2592. The path is located a distance away from the fixed pivotpoint 2592 that is substantially equal to the distance between the fixedpivot point 2592 and the rotating pivot point 2592. Similarly, pivotpoint 2591, which is located along the length of the dog bone link 2519also travels in an arcuate path around fixed pivot point 2592 that isparallel to that traveled by pivot point 2599. The path is located adistance away from the fixed pivot point 2592 that is substantiallyequal to the distance between the fixed pivot point 2592 and therotating pivot point 2591. The pivot point 2571 between the mountingbracket 2570 and the rear frame 2514 travels along a linear path that isdefined by the pivot link assemblies 2516, 2518.

The ICC and the IC for this example vary and migrate throughout the pathtraveled by the wheel. As shown in FIGS. 24A-24D, the ICC and the ICmove in different directions, with the IC defining a substantiallystraight line that extends downwardly and rearwardly from the bracket2570 and the ICC defining a curve that extends rearwardly from thebracket 2570. As is shown in FIGS. 24A-D, the curve defined by the ICCbecomes increasingly concave as the rear wheel travels upwardly,resulting in the aforementioned wheel path in which the curvature of thepath changes as the wheel approaches the highest point in its path.Notably, the distance traveled by the wheel in the y-direction is verylarge as compared to the distance traveled by the bracket 2570 along thex-axis.

FIGS. 25A-25D illustrate another application of a linkage system 2315.As consistent with other examples described herein, the linkage system2315 includes first and second pivot link assemblies 2316, 2318 that arearranged in a crossed configuration. As shown in FIGS. 25B-25D, thefront ends of the pivot link assemblies 2316, 2318 may be attached atangles to a mounting bracket 2317, which in turn, may be attached eitherdirectly or indirectly to a supported object, such as a television 2301.The rear ends of the pivot link assemblies 2316, 2318 may be attached,either directly or indirectly, to a supporting object 2321, such as awall, or other object. As discussed above with respect to otherexamples, the transverse orientation of the pivot link assemblies 2316,2318 serves to confine the motion of the television 2301 relative to thewall or object 2321 to a substantially linear path along the z-axis.This motion is best illustrated in FIGS. 25B and 25C, which respectivelyillustrate the television 2301 in an extended position further away fromthe wall 2321, and in a retracted position closer to the wall 2321.

In some examples, additional pivotal attachments may be provided toallow for rotation of the television 2301, mounting bracket 2317 and/orpivot link assemblies 2316, 2318 relative to one another. For example,in the illustrated example, the television 2301 is joined to a supportarm 2322 that is pivotally coupled to the mounting bracket 2317 to allowthe television 2301 to pivot relative to the mounting bracket 2317. Asbest shown in FIGS. 25B and 25C, this may allow for tilting the screenof the television 2301 along the X-Z plane. Additionally, the mountingbracket 2317 may include a rotatable portion 2323 rotatably coupled to abase portion 2324 to allow for rotation of the television 2301 aroundthe base portion 2324. As best shown in FIG. 25D, this may allow forrotating the screen of the television 2301 along the X-Y plane.

In other examples, the lengths of the links of the pivot link assemblies2316, 2318 may be changed to increase or decrease the distance of thetelevision 2301 from the supporting object or wall 2321. Additionally,the attachment points of the ends of the pivot link assemblies 2316,2318 may be changed. In further examples, one or both of the pivot linkassemblies 2316, 2318 may include more than two links, which may allowfor further extension of the pivot link assemblies 2316, 2318 along thez-axis.

It will be appreciated from the above noted description of the variousarrangements and examples of the present disclosure that a rearsuspension system for a bicycle has been described which includes afirst link assembly and a second link assembly. The rear suspensionsystem can be formed in various ways and operated in various mannersdepending upon a user's desired rear wheel path and leverage ratiocurve. It will be appreciated that the features described in connectionwith each arrangement and example of the disclosure are interchangeableto some degree so that many variations beyond those specificallydescribed are possible. It should also be understood that the abovedescribed component parts of the rear suspension need not be connectedwith the bicycle in the manners described and depicted above, and assuch, can be connected with the frame and with each other in variousadditional locations. It should also be understood that the physicalshapes and relative lengths of the rear suspension components are notlimited to that which has been depicted and described herein.

Although various representative examples of this disclosure have beendescribed above with a certain degree of particularity, those skilled inthe art could make numerous alterations to the disclosed exampleswithout departing from the spirit or scope of the inventive subjectmatter set forth in the specification and claims. All directionalreferences (e.g., upper, lower, upward, downward, left, right, leftward,rightward, top, bottom, above, below, vertical, horizontal, clockwise,and counterclockwise) are only used for identification purposes to aidthe reader's understanding of the examples of the present disclosure,and do not create limitations, particularly as to the position,orientation, or use of the invention unless specifically set forth inthe claims. Joinder references (e.g., attached, coupled, connected, andthe like) are to be construed broadly and may include intermediatemembers between a connection of elements and relative movement betweenelements. As such, joinder references do not necessarily infer that twoelements are directly connected and in fixed relation to each other.

In some instances, components are described with reference to “ends”having a particular characteristic and/or being connected with anotherpart. However, those skilled in the art will recognize that the presentinvention is not limited to components which terminate immediatelybeyond their points of connection with other parts. Thus, the term “end”should be interpreted broadly, in a manner that includes areas adjacent,rearward, forward of, or otherwise near the terminus of a particularelement, link, component, part, member or the like. In methodologiesdirectly or indirectly set forth herein, various steps and operationsare described in one possible order of operation, but those skilled inthe art will recognize that steps and operations may be rearranged,replaced, or eliminated without necessarily departing from the spiritand scope of the present invention. It is intended that all mattercontained in the above description or shown in the accompanying drawingsshall be interpreted as illustrative only and not limiting. Changes indetail or structure may be made without departing from the spirit of theinvention as defined in the appended claims.

The foregoing has been generally described with respect to particularexamples and methods of manufacture. It will be apparent to those ofordinary skill in the art that certain modifications may be made withoutdeparting from the spirit or scope of this disclosure. For example, afiber other than carbon may be used as a strengthening or stiffeningelement. As one example, certain metals may be used instead, or anothertype of plastic may be used. Accordingly, the proper scope of thisdisclosure is set forth in the following claims.

What is claimed is:
 1. A bicycle comprising: a front frame; a rear frameoperably associated with the front frame and pivotally coupled to amounting bracket; and a suspension system operably coupled to the frontframe and to the rear frame and comprising a shock assembly; wherein therear frame is pivotally coupled to the suspension system so as to definea pivot point between the rear frame and the suspension system, andwherein the pivot point and at least a portion of the mounting bracketare configured to travel along a substantially linear path in a firstdirection and in a substantially linear path in a second directionopposite the first direction as the shock assembly articulates.
 2. Thebicycle of claim 1, further comprising a wheel, wherein the suspensionsystem causes the pivot point to travel along the substantially linearpath in the first direction and in the second direction as the wheeltravels in an upward direction relative to the front frame.
 3. Thebicycle of claim 1, wherein the suspension system comprises: a firstpivot link assembly including a first link configured to rotate around afirst pivot point, the first pivot point having a first axis of rotationthat is non-orthogonal to a longitudinal axis of the frame; and a secondpivot link assembly including a second link configured to rotate arounda second pivot point, the second pivot point having a second axis ofrotation that is non-orthogonal to the longitudinal axis of the frame.4. The bicycle of claim 1, wherein the rear frame is pivotally coupledto a mounting bracket.
 5. The bicycle of claim 4, wherein the mountingbracket is configured to travel along the substantially linear path inthe first direction and in the second direction opposite the firstdirection as the shock assembly transforms between an uncompressed stateto a fully compressed state.
 6. The bicycle of claim 1, wherein thepivot point is configured to travel along the substantially linear pathin the first direction as the shock assembly transforms from anuncompressed state to a partially compressed state.
 7. The bicycle ofclaim 1, wherein the pivot point is configured to travel along thesubstantially linear path in the second direction as the shock assemblytransforms from a partially compressed state to a fully compressedstate.
 8. The bicycle of claim 1, wherein the pivot point is configuredto travel along the substantially linear path in the first direction asthe shock assembly transforms from a fully compressed state to apartially compressed state.
 9. The bicycle of claim 1, wherein the pivotpoint is configured to travel along the substantially linear path in thesecond direction as the shock assembly transforms from a partiallycompressed state to an uncompressed state.
 10. The bicycle of claim 1,wherein the rear frame is pivotally coupled to a link.
 11. The bicycleof claim 10, wherein the link is further pivotally coupled to the frontframe.
 12. The bicycle of claim 10, wherein the link is furtherpivotally coupled to the shock assembly.
 13. The bicycle of claim 10,wherein one end of the shock assembly is configured to travel along anarcuate path defined by the link.
 14. The bicycle of claim 10, whereinthe rear frame is configured to travel along an arcuate path defined bythe link.
 15. A bicycle comprising: a front frame; a rear frame that ispivotally coupled to a link which is further pivotally coupled to atleast one of the front frame or a shock assembly; and a suspensionsystem operably coupled to the front frame and to the rear frame andcomprising the shock assembly; wherein the rear frame is pivotallycoupled to the suspension system so as to define a pivot point betweenthe rear frame and the suspension system, and wherein the pivot point isconfigured to travel along a substantially linear path in a firstdirection and in a substantially linear path in a second directionopposite the first direction as the shock assembly articulates.
 16. Abicycle comprising: a front frame; a rear frame operably associated withthe front frame; and a suspension system operably coupled to the frontframe and to the rear frame and comprising a shock assembly, a firstpivot link assembly including a first link configured to rotate around afirst pivot point, the first pivot point having a first axis of rotationthat is non-orthogonal to a longitudinal axis of the frame; and a secondpivot link assembly including a second link configured to rotate arounda second pivot point, the second pivot point having a second axis ofrotation that is non-orthogonal to the longitudinal axis of the frame;wherein the rear frame is pivotally coupled to the suspension system soas to define a pivot point between the rear frame and the suspensionsystem, and wherein the pivot point is configured to travel along asubstantially linear path in a first direction and in a substantiallylinear path in a second direction opposite the first direction as theshock assembly articulates.